DE102004038287A1 - Multi-stage automatic transmission - Google Patents

Abstract

A multi-stage automatic transmission has a drive shaft (AN), an output shaft (AB), a dual planetary gearset (VS), a main gearset (HS) designed as a coupled planetary gear set with at least three uncoupled input elements and an output element, and six shift elements (A to F) ), by the pairwise closing at least eight forward gears are switchable on. An input element of the transfer gearset (VS) is connected to the drive shaft (AN). An output element of the transfer gearset (VS) rotates at a speed smaller than the input speed of the drive shaft (AN). An element of the transfer gearset (VS) is fixed to a transmission housing (GG). The first input element of the main gearset (HS) is connected via a second switching element (B) to the output element of the transfer gearset (VS) connectable via a third switching element (C) and via a sixth switching element (F) to the drive shaft (AN) connectable. The second input element of the main gearset (HS) can be connected via a first switching element (A) to the output element of the transfer gearset (VS). The third input element of the main gearset (HS) can be fixed via a fourth shift element (D) and can be connected to the drive shaft (AN) via a fifth shift element (E). The output element of the main gearset (HS) is connected to the output shaft (AB). The fifth and sixth switching element (E, F) form an assembly, comprising a for ...

Description

The The invention relates to a multi-stage automatic transmission according to the Qberbegriff of claim 1

Automatic transmissions with several, without group switching switchable gears are widely known. From the US 5,106,352 a 6-speed automatic transmission is known in which a simple planetary gearset is arranged coaxially to a designed as Ravigneaux planetary gear two-staged four-shaft main gear and five switching elements are provided. Here, the front-mounted planetary is designed as a non-switchable Reduzierstufe with fixed to a gear housing sun gear whose output speed is smaller than the speed of a drive shaft of the automatic transmission and two clutches on two different elements of the main gear is transferable, with one of these two elements in addition to a first brake on the transmission housing can be fixed. This input element of the main gearset, which can be connected either to the output element of the transfer gearset or fixed to the transmission housing, is hereinafter referred to as "first input element of the main gearset". Accordingly, the other input element of the main gearset, which is also connectable to the output element of the planetary gearset, hereinafter referred to as "second input element of the main gearset". The speed of the drive shaft is transferable via a third clutch to a third input element of the main gearset, said third element via a second brake and on the transmission housing can be fixed. A fourth element of the main gearset forms the output element of the main gearset and is only permanently connected to a drive shaft of the automatic transmission.

Several alternative component arrangements to this in the US 5,106,352 described automatic transmissions are for example from the US 6,139,463 and the DE 102 10 348 A1 known.

In the not yet published German patent application DE 10221095.0 The applicant is a further development of the in US 5,106,352 known 6-speed automatic transmission to a 7-speed automatic transmission described. Opposite the US 5,106,352 the planetary gearset is designed as a simple, switchable plus planetary gear in Doppelplanetenbauweise and added an additional sixth switching element. A web of the planetary gearset forms the integral with the drive shaft of the automatic transmission input element of the planetary gearset. A sun gear of the planetary gear set is over the opposite US 5,106,352 additional sixth switching element fixed to a transmission housing. Accordingly, a ring gear of the planetary gearset forms the connectable to two different elements of the main gear output element of the planetary gearset and rotates at a speed less than or equal to the speed of the drive shaft. For this kinematic coupling of the individual wheelset elements and switching elements discloses the DE 10221095.0 numerous different arrangement variants of the transmission components relative to each other.

In JP 2001/182785 A is a further development of the US 5,106,352 known 6-speed automatic transmission to an 8-speed automatic transmission described. Opposite the US 5,106,352 In this case, the planetary gearset is designed as a simple, non-switchable plus planetary gear in Doppelplanetenbauweise and added an additional sixth switching element. A web of the planetary gearset forms the integral with the drive shaft of the automatic transmission input element of the planetary gearset. A sun gear of the planetary gear set is fixed to a transmission housing. Accordingly, a ring gear of the planetary gearset forms the connectable to two different elements of the main gear output element of the planetary gearset and always rotates at a speed less than the speed of the drive shaft. About that over the US 5,106,352 additional sixth switching element is the - optionally connectable to the output element of the planetary gearset or fixable on the transmission housing - first input element of the main gearset now optionally also connectable to the drive shaft of the transmission. With regard to the spatial arrangement of the switching elements relative to each other and relative to the Planetenradsätzen is proposed in JP 2001/182785 A, the two switching elements, via which the first and second input element of the main gearset with the ring gear of the planetary gearset are connectable, together with the opposite of the US 5,106,352 to arrange additional sixth switching element as an assembly axially between the front-mounted and the main gearset. This is already out of the US 5,106,352 known (fifth) switching element, via which the drive shaft is connectable to the third input element of the main gearset, arranged on the opposite side of the main gearset, ie also on the side facing away from the planetary gearset side of the main gearset. Furthermore, JP 2001/182785 A, which teaches against the US 5,106,352 additional sixth switching element within said assembly spatially over radially to arrange the switching element, via which first input element of the main gearset with the ring gear of the transfer gearset is connectable.

In the not yet published German patent application DE 10318565.8 the applicant is described an improved component assembly of the known from JP 2001/182785 A 8-speed automatic transmission. To comply with the underlying basic design of the 6-speed automatic transmission US 5,106,352 only comparatively few structural changes have to be made in the DE 10318565.8 proposed to maintain the known from the 6-speed automatic transmission spatial position of planetary gearset, Ravigneaux main gear and the first five switching elements in the gearbox relative to each other and that against the US 5,106,352 to arrange additional sixth switching element in the transmission housing on the side of the transmission, which faces a drive motor, spatially seen between a drive-side gear housing wall and first switching element via which the output element of the ballast Planetaryadsatzes with the second input element of the main gear is connectable, but also spatially between said drive side gear housing wall and the front-mounted planetary gear set. That opposite the US 5,106,352 additional sixth switching element is thus arranged on the side facing away from the main gearset of the planetary gearset.

The present invention is based on the object that in JP 2001/182785 A and the DE 10318565.8 to further develop specified multi-speed automatic transmissions with eight forward gears and to provide alternative component arrangements for the planetary gear sets and the six shift elements for.

These Task is by a the features of claim 1 exhibiting Multi-stage automatic transmission solved. Advantageous embodiments and developments of the invention will become apparent from the dependent claims.

The invention is based on that in JP 2001/182785 A or not yet published German patent application DE 10318565.8 the Applicant described transmission scheme for a multi-stage automatic transmission with at least eight forward gears, comprising a drive shaft, an output shaft, designed as a double planetary gearset, a coupled as a planetary gear with at least three non-coupled input elements and an output element formed main gear, and at least six switching elements. By selectively closing each of two of the switching elements, a rotational speed of the drive shaft can be transmitted to the output shaft such that only one switching element is opened and another switching element is closed to switch from one gear to the next higher or next lower gear from the currently operated switching elements. The entire disclosure of the not yet prepublished German patent application DE 10318565.8 The applicant is expressly also part of the disclosure of the present invention.

One Input element of the transfer gear is constantly with the drive shaft connected. An output element of the transfer gear always rotates at a speed less than the speed of the drive shaft. A third Element of the Vorschaltradsatzes is fixed to a gear housing. The output speed of the Vorschaltradsatzes is about two switching elements two different input elements of the main gearset transferable. The speed of the drive shaft is about two other switching elements also transferable to two different input elements of the main gearset. The Output element of the main gear is constantly with the output shaft connected.

In a preferred embodiment of this transmission scheme as 8-speed automatic transmission forms a (coupled) bridge the Vorschaltradsatzes whose always connected to the drive shaft input element, a ring gear of the Vorschaltradsatzes whose with two different input elements of the Main gearset connectible output element, and a sun gear of the Vorschaltradsatzes whose fixed to the gearbox third element. Vorschalt- and main gear are arranged coaxially to each other. The main gear set can be designed as a two-track, four-shaft gearbox a "Ravigneaux planetary gear set" be executed, with a first sun gear as the first input element of the main gearset, which optionally with the ring gear of the transfer gear or the Drive shaft can be connected or fixed to the transmission housing, with a second sun gear as a second input element of the main gearset, which is connectable to the ring gear of the transfer gear, with a (coupled) web as the third input element of the main gearset, which optionally connectable to the drive shaft or fixed to the transmission housing is, as well as with a ring gear as an output element of the main gear, which is always connected to the output shaft.

• • ein Eingangselement des ersten Schaltelementes mit dem Ausgangselement des Vorschaltradsatzes verbunden,
• • ein Ausgangselement des ersten Schaltelementes mit dem zweiten Eingangselement des Hauptradsatzes verbunden,
• • ein Eingangselement des zweiten Schaltelementes mit dem Ausgangselement des Vorschaltradsatzes verbunden,
• • ein Ausgangselement des zweiten Schaltelementes mit dem ersten Eingangselement des Hauptradsatzes verbunden,
• • ein Eingangselement des dritten Schaltelementes mit dem Getriebegehäuse verbunden,
• • ein Ausgangselement des dritten Schaltelementes mit dem ersten Eingangselement des Hauptradsatzes verbunden,
• • ein Eingangselement des vierten Schaltelementes mit dem Getriebegehäuse verbunden,
• • ein Ausgangselement des vierten Schaltelementes mit dem dritten Eingangselement des Hauptradsatzes verbunden,
• • ein Eingangselement des fünften Schaltelementes mit der Antriebswelle verbunden,
• • ein Ausgangselement des fünften Schaltelementes mit dem dritten Eingangselement des Hauptradsatzes verbunden,
• • ein Eingangselement des sechsten Schaltelementes mit der Antriebswelle verbunden,
• • ein Ausgangselement des sechsten Schaltelementes mit dem ersten Eingangselement des Hauptradsatzes verbunden, sowie
• • das Ausgangselement des Hauptradsatzes ständig mit der Abtriebswelle verbunden.

In this case, then

• An input element of the first switching element is connected to the output element of the transfer gearset,
• An output element of the first switching element tes connected to the second input element of the main gear,
• An input element of the second switching element connected to the output element of the transfer gear,
• An output element of the second switching element is connected to the first input element of the main gearset,
• An input element of the third switching element connected to the transmission housing,
• An output element of the third switching element connected to the first input element of the main gearset,
• An input element of the fourth switching element connected to the transmission housing,
• An output element of the fourth switching element is connected to the third input element of the main gearset,
• An input element of the fifth switching element connected to the drive shaft,
• An output element of the fifth shift element is connected to the third input element of the main gearset,
• An input element of the sixth switching element connected to the drive shaft,
• • An output element of the sixth switching element connected to the first input element of the main gearset, as well
• • The output element of the main gear is constantly connected to the output shaft.

Of the Main gearset can also be used as a two-track four-shaft transmission be formed two coupled Einsteg planetary gear sets, wherein for example, optionally with the ring gear of the transfer gear or the drive shaft connectable or fixable on the transmission housing first input element of this main gear by a sun gear of the first of these two single planet gear sets of the main gear and a bridge connected to this first sun gear of the main gearset of the second of these two single-gear planetary gear sets of the main gearset is, and wherein the connectable to the ring gear of the transfer gear second input element of this main gear by a sun gear formed of the second of the two single-planetary gear sets of the main gear is, and optionally being connectable to the drive shaft or festsetzbare on the transmission housing third input element of the main gear set by a bridge of the first the two entry planetary gear sets of the main gear and one with this first bridge of the main gear connected ring gear of the second of the two input planetary gear sets of Main gear is formed, and wherein a ring gear of the first of two single-entry planetary gear sets the main gear as the output element of this main gear always with the output shaft is connected. In this case, the connection corresponds the input and output elements of the six switching elements to the three input elements the main gearset previously described using the example of Ravigneaux main gear Connectivity.

• • das Eingangselement des dritten Schaltelementes ist mit dem Getriebegehäuse verbunden,
• • das Ausgangselement des dritten Schaltelementes ist mit dem ersten Eingangselement des Hauptradsatzes oder einem in einem Drehzahlplan zu diesem ersten Eingangselement benachbarten Eingangselement des Hauptradsatzes verbunden,
• • das Eingangselement des sechsten Schaltelementes ist mit der Antriebswelle verbunden,
• • das Ausgangselement des sechsten Schaltelementes ist mit dem ersten Eingangselement des Hauptradsatzes oder einem in dem Drehzahlplan zu diesem ersten Eingangselement benachbarten Eingangselement des Hauptradsatzes verbunden.

The main gearset can for example be designed as a three-way five-shaft transmission with three coupled Einsteg-Planetenradsätzen, or as a reduced three-way five-shaft transmission with three coupled Einsteg planetary gear sets, in which at least two of these individual planetary gear sets via a common web and a another common central wheel (ie either via their sun gears or via the ring gears) coupled together ("reduced") are. Analogously, the main gearset can also be configured, for example, as a "reduced four-shaft six-shaft transmission in which the four individual planetary gear sets coupled together are combined in such a way that the main gearset has only two webs six switching elements to the input elements of a main gearset of the type "two-track four-shaft planetary gear offer different possibilities with regard to the kinematic connection of the input and output elements of the third and sixth switching element to the individual main gearset elements, in which case:

• The input element of the third switching element is connected to the transmission housing,
• The output element of the third shift element is connected to the first input element of the main gearset or to an input element of the main gearset adjacent to this first input element in a speed control plan,
• The input element of the sixth switching element is connected to the drive shaft,
• • The output element of the sixth switching element is connected to the first input element of the main gearset or an input element of the main gearset which is adjacent to this first input element in the speed diagram.

In all mentioned embodiments are in the first forward gear the first and fourth switching element, in the second forward gear the first and third switching element, in the third forward gear the first and second switching element, in the fourth forward gear, the first and sixth Switching element, in the fifth forward gear the first and fifth Shift element, in the sixth forward gear the fifth and sixth switching element, in the seventh forward gear, the second and fifth switching element and in the eighth forward gear the third and fifth Switching element closed. In reverse are the fourth switching element and additionally either the second or the sixth switching element closed.

According to the invention It is now proposed that the fifth switching element, over which the drive shaft of the transmission with the third input element the main gear is connectable, and the sixth switching element, via which the drive shaft of the transmission with the first or a (in the Speed plan for this first input element of the main gearset adjacent) fourth input element of the main gearset connectable is to form an assembly comprising one for the fifth and sixth switching element common plate carrier, one each disc pack for the fifth and sixth switching element and a respective servo device for the fifth and sixth switching element for actuation the respective disk set of the fifth and sixth switching element. It forms the for the fifth and sixth switching element common plate carrier both the input element of the fifth Switching element and the input element of the sixth switching element.

In a first advantageous embodiment of the fifth and sixth switching element formed assembly is proposed that this assembly spatially seen at least predominantly on the side facing away from the main gearset of the transfer gear is arranged. It can the first switching element, via which the output element of the transfer gearset with the second Input element of the main gear is connectable, and the second Switching element, via which the output element of the transfer gearset with the first Input element of the main gear is connectable, at least predominantly be arranged on the side of the transfer gear, the by the fifth and the sixth switching element formed opposite said assembly, in which case the first switching element is preferably closer to the transfer gearset is arranged as the second switching element. In such a spatial Arrangement of the first, second, fifth and sixth switching element can on the one hand with the first or fourth input element of the main gearset connected output element of the sixth switching element the Vorschaltradsatz and the first and radially overlap second switching element in the axial direction, on the other hand, also connected to the third input element of the main gearset Output element of the fifth Switching element said output element of the sixth switching element radially at least partially overlap in the axial direction. It is also at such a spatial Arrangement of the first, second, fifth and sixth switching element expedient when the third switching element, via which the first input element of the main gearset or a (in the speed plan adjacent to this first input element of the main gearset) fourth input element of the main gearset fixed to the gear housing is, and / or the fourth switching element, via which the third input element of the main gearset can be fixed to the transmission housing, on the Side of the transfer gear is arranged, that by the fifth and the sixth switching element formed opposite assembly.

In a second advantageous embodiment of the fifth and sixth switching element formed assembly is proposed that this assembly spatially seen at least predominantly in a range axially between the transfer gearset and the main gearset is arranged. In this case, the assembly of the fifth and sixth switching element spatial Seen at least partially radially under a disc pack of be arranged second switching element, in which case with the first Input element of the main gear connected output element of the second switching element, the said assembly of the fifth and sixth Switching element in the axial direction radially at least partially overlaps. Also, the assembly of the fifth and sixth switching element spatially Seen at least partially radially under a disc pack of be arranged first switching element. In such a spatial Arrangement of the first, second, fifth and sixth switching element, it is expedient if the third and / or Fourth switching element arranged on the side of the main gear are opposite to the transfer gear.

In a third advantageous embodiment of the fifth and sixth switching element formed assembly is proposed that this assembly spatially seen at least predominantly on the side of the main gearset facing away from the transfer gearset is arranged. It can the first and second switching element at least predominantly on the side of Hauptradsatzes be arranged, the said assembly of the fifth and opposite sixth switching element. In such a spatial Arrangement of the fifth and sixth switching element, it is expedient if the third and / or fourth switching element at least predominantly are arranged on the same side of the main gear, at the also the mentioned assembly of the fifth and sixth switching element is arranged.

In all these three embodiments of the assembly formed by the fifth and sixth switching element, the disk set of the fifth switching element can either be arranged either on a larger diameter than the disk set of the sixth switching element (in this case spatially preferably at least partially radially over said disk set of sixth switching element), or on a smaller diameter than the plate pack the sixth switching element (in this case spatially preferably at least partially radially below said disk set of the sixth switching element), or arranged on an at least similar diameter as the disk set of the sixth switching element (in this case spatially preferably closer to the transfer gearset than said Disc pack of the sixth switching element).

The Invention and its advantageous embodiments and developments will be explained in more detail below with reference to the figures, wherein the reference numerals comparable components in all figures also referred to like are. Show it:

1A a transmission scheme according to the generic state of the art;

1B a circuit diagram of the transmission according to 1 ;

1C a speed plan of the transmission according to 1 ;

2 an exemplary first inventive transmission scheme;

3 an exemplary second transmission scheme according to the invention;

4 an exemplary third transmission scheme according to the invention;

5 an exemplary fourth transmission scheme according to the invention;

6 an exemplary fifth transmission scheme according to the invention;

7 an exemplary sixth transmission scheme according to the invention;

8th an exemplary seventh transmission scheme according to the invention;

9 an exemplary eighth inventive transmission scheme

10 an exemplary ninth transmission scheme according to the invention;

11 an exemplary tenth transmission scheme according to the invention; and

12 a design variant of the tenth invention according to the transmission scheme 11 ,

For a better understanding of the invention underlying the prior art is first explained. 1A shows the gearbox of the generic state of the art according to DE 10318565.8 . 1B the corresponding circuit diagram. In 1A is denoted by AN a drive shaft of the automatic transmission, which is operatively connected to a (not shown) drive motor of the automatic transmission, in the illustrated example via a torque converter with torsional damper and lockup clutch. AB is a koxial to the drive shaft arranged on the output shaft of the automatic transmission, which is operatively connected to at least one drive axle of the motor vehicle. Of course, instead of the torque converter and a friction clutch may be arranged as a starting element of the automatic transmission between the drive motor and automatic transmission. Also, the drive motor could only be connected via a simple torsional damper or a dual mass flywheel or a rigid shaft to the drive shaft AN of the transmission, in which case a disposed within the automatic transmission Reibschaltelement must be designed as a starting element of the transmission.

The Automatic transmission has a transfer gearset VS and a coaxial next to (but not next to) this transfer gearset VS arranged main gearset HS. The transfer gearset VS is as Plus planetary gear set in double planetary design, with a ring gear HO_VS, with a sun gear SO_VS, and with a web formed by two individual webs ST_VS, on the inner planetary gears P1_VS, which mesh with the sun gear SO_VS, and outer planet gears P2_VS, the with the inner planet wheels Meshing P1_VS and the ring gear HO_VS, are rotatably mounted. This gearset works VS as a non-switchable Reduzierstufe and generates an output speed, which is smaller in magnitude than an input speed of the drive shaft ON of the automatic transmission. For this purpose, the sun gear SO_VS of the transfer gearset VS on a gearbox GG fixed and the bridge ST_VS constantly with the drive shaft Connected to. The ring gear HO_VS thus forms the output element of the transfer gearset VS and is connected via two switching elements A, B with individual input elements of the main gearset HS connectable.

The main gearset HS is designed as a coupled two-track four-shaft planetary gear, with three uncoupled input elements and an output element, in the form of a Ravigneaux gear set with two sun gears S1_HS and S2_HS, a ring gear HO_HS and a coupled web ST_HS, at the long planet gears P1_HS , which mesh with the first sun gear S1_HS and the ring gear HO_HS, and kur The planetary gears P2_HS, which mesh with the second sun gear S2_HS and the long planetary gears P1_HS, are rotatably mounted. In this case, the first sun gear S1_HS forms the first input element of the main gearset HS, the second sun gear S2_HS the second input element of the main gearset HS, the coupled web ST_HS the third input element of the main gearset HS and the ring gear HO_HS the output element of the main gearset HS.

The Automatic transmission has a total of six switching elements A to F. The switching elements A, B, E and F are designed as a coupling, the switching elements C and D as a brake. This is the second sun gear S2_HS of the main gearset HS via the first switching element A with the ring gear HO_VS of Vorschaltradsatzes VS connectable. Weitehin this is the first sun S1_HS of the Main gearset HS over the second switching element B with the ring gear HO_VS of Vorschaltradsatzes VS connectable, over the third switching element C to the transmission housing GG fixable and on the sixth switching element F with the drive shaft AN connectable. Weitehin For this purpose, the web ST_HS of the main gearset HS via the fourth switching element D on the gearbox GG determinable and over the fifth switching element E can be connected to the drive shaft AN. As a result of this connection the individual elements of the main gearset HS to the individual switching elements is the bridge ST_HS of the Hautradsatzes HS so by a simultaneous Shut down of the fifth and sixth switching element E, F also with the first sun S1_HS the main gearset HS connectable. The ring gear HO_HS of the main gearset HS is constantly and exclusively connected to the output shaft AB.

1B shows a circuit diagram of the in 1A illustrated multi-stage automatic transmission. There are a total of eight forward gears groupschaltungsfrei switchable, so such that for switching from one gear in the next higher or next lower gear from the currently operated switching elements only one switching element is opened and another switching element is closed. In first gear "1" clutch A and brake D are closed, in second gear "2" clutch A and brake C, in third gear "3" clutches A and B, in fourth gear "4" clutches A and F, in fifth gear "5" clutches A and E, in sixth gear "6" clutches E and F, in seventh gear "7" clutches B and E, and in eighth gear "8" brake C and clutch E. In a first reverse gear "R1" clutch B and brake D are closed. It can also be provided a second reverse gear "R2", are closed in the clutch F and brake D. 1C shows a speed plan of the in 1A illustrated multi-stage automatic transmission. 1C shows a speed plan of the in 1A illustrated multi-stage automatic transmission.

Coming back to 1A , the disk packs and the input and output elements of the switching elements are uniformly designated. So is the disk set of the first switching element A with 100 denotes the input element of the first switching element A with 120 , The output element of the first switching element A with 130 , as well as a servo device for actuating the disk pack 100 of the first switching element A with 110 , Accordingly, the disk packs of the other switching elements B, C, D, E and F with 200 . 300 . 400 . 500 and 600 denotes the input elements of the other switching elements B, E and F with 220 . 520 and 620 , Accordingly, the output elements of the other switching elements B, C, D, E and F with 230 . 330 . 430 . 530 and 630 and the servos of the other clutches B, E and F for actuating their respective disc packs 200 respectively. 500 respectively. 600 With 210 . 510 and 610 ,

With regard to the spatial arrangement of the switching elements and wheelsets relative to each other within the designated GG transmission housing teaches the DE 10318565.8 The following: The trained as a clutch fifth switching element E is spatially arranged axially between the transfer gearset VS and main gearset HS, axially immediately adjacent to the transfer gearset VS. The likewise designed as a clutch second switching element B is also arranged axially between the transfer gearset VS and main gearset HS, wherein the disk set 200 spatially seen in about radially above the disk pack 500 the clutch E is arranged and the servo device 210 the clutch B axially adjacent to the clutch E on the side facing away from the transfer gearset VS side. Axially in the direction of the main gearset HS close to the clutch B first formed as a brake third switching element C, then designed as a brake fourth switching element D and then the main gearset HS. The slat package 100 formed as a clutch first switching element A is spatially arranged approximately above the transfer gearset VS. The servo device 110 This clutch A is at least predominantly arranged on the side facing away from the main gearset HS side of the transfer gearset VS. On the side of the servo device facing away from the transfer gearset VS 110 the clutch A, spatially seen axially between the clutch A and a drive-side housing housing fixed housing wall GW, ie on the side facing away from the main gearset HS side of clutch A and transfer gearset VS, designed as a clutch sixth switching element F is arranged.

As an exemplary embodiment of a servo direction of a switching element is in 1A the servo device 610 of the sixth switching element F in more detail. So this is the servo 610 innenehalb arranged a cylindrical plate carrier, which is the input element 620 forms the clutch F and accordingly rotates always at rotational speed of the drive shaft AN of the transmission. The servo device 610 has a pressure chamber 611 on, by a lateral surface portion of the disk carrier of the clutch F and a piston 614 the servo device 610 is formed. When pressurizing this pressure chamber 611 the piston moves 614 against the force of a here exemplified as a diaphragm spring return element 613 the servo device 610 axially in the direction of the transfer gearset VS and actuates or closes the disk set 600 the clutch F. For preferably complete compensation of a dynamic pressure of the rotating pressure chamber 611 indicates the servo 610 In addition, a pressureless fillable with lubricant pressure compensation chamber 612 on, passing through an area of the piston 614 and a baffle plate 615 is formed. The input element 620 is rotatably mounted on a gear housing fixed hub GN, which extends from the gear housing fixed housing wall GW in the interior of the gear housing GG axially in the direction of the transfer gearset VS to the sun gear SO_VS of the transfer gearset VS and is rotationally connected to this sun gear SO_VS. Accordingly, this gearbox fixed hub GN also channels for supplying pressure and lubricant to the pressure chamber or pressure compensation chamber of the clutch F.

Based 2 Now, a first exemplary transmission scheme according to the present invention will be explained. As in the generic state of the art according to 1 the automatic transmission according to the invention comprises a drive shaft AN, an output shaft AB, a planetary gearset VS constructed as a single planetary gearset, a multi-element main gearset HS formed from coupled planetary gear sets, and six shifting elements A to F. Preferably, by selectively closing each of these six Switching elements A to F, a speed of the drive shaft AN on the wheelsets VS, HS transmittable in at least eight different forward gears, with each gear change from a gear in the next higher or next lower gear always only one previously switched switching element opened and not previously switched Switching element is closed. The transfer gearset VS and the main gearset HS are arranged coaxially with one another. By way of example, the drive shaft AN and the output shaft AB are coaxial with each other, but can also be parallel to the axis or at an angle to each other by a comparatively simple modification. The kinematic coupling of transfer gearset VS and main gearset HS to the switching elements A to F and to the drive and output shafts AN, AB has been essentially of 1 taken over, so that also for the first inventive transmission according to 2 in the 1B shown switching logic applies.

A detail difference to 1 relates to the configuration of the main gearset HS, which is now exemplified as a "two-track unit reduced three-way, five-shaft planetary gear" with four independent input elements and an output element is executed this "new" main gearset HS according to 2 is formed of three individual coupled planetary gear sets, again two of these three individual planetary gear sets are combined as a planetary gear, which is then coupled to the remaining single planetary gear set. In this case, the "new" main gearset HS comprises three sun gears S1_HS, S2_HS and S3_HS, only two ring gears H13_HS and H2_HS, as well as only two webs ST13_HS and ST2_HS, each with planetary gears P13_HS and P2_HS rotatably mounted thereon. The second sun gear S2_HS, the second bridge ST2_HS, the short planetary gears P2_HS and the second ring gear H2_HS are assigned to the remaining individual planetary gearset of the main gearset HS, these short planetary gears P2_HS meshing with the second sun gear S2_HS and the second ring gear H2_HS of the main gearset HS. The first and third sun gear S1_HS and S3_HS, the coupled web ST13_HS, the long planetary gears P13_HS and the coupled ring gear H13_HS are associated with the coupled planetary gearset of the main gearset HS, these long planetary gears P13_HS with both sun gears S1_HS and S3 HS and with the coupled ring gear H13_HS of the main gearset HS comb. In principle, the so-described coupled planetary gearset of the main gearset HS can thus also be understood as a single planetary gear with a split sun gear. This "division of said sun gear into two individual sun gears (S1_HS, S3_HS) in turn is important to the kinematic coupling of the input elements of the main gearset HS to the various switching elements A to F and the kinematic coupling of the output element of the main gearset HS to the output shaft AB of Getriebes, as well as from the generic state of the art according to 1 given to be able to represent now in connection with the component assembly according to the invention described below. Spatially seen, the single sun gear S2_HS having single planetary gearset of the main gearset HS is arranged on the side of the main gearset HS away from the transfer gearset, whereas the third sun gear S3_HS is arranged on the side of the main gearset HS close to the transfer gearset. The first sun gear S1_HS of the Main gearset HS is thus arranged axially between the other sun gears S3_HS and S2_HS of the main gearset HS.

The transfer gearset VS includes as in 1 a sun gear SO_VS, a coupled bridge ST VS with inner and outer planetary gears P1_VS, P2_VS rotatably mounted thereon and a ring gear HO_VS. The sun gear SO_VS is fixed to a gearbox GG rotationally fixed to the hub GN, which extends from a gear housing fixed housing wall GW in the transmission interior in the direction of the transfer gearset VS, set. The said housing wall GW here forms an outer wall of the transmission, which is arranged on the one hand on the side facing away from the main gearset HS side of the transfer gearset VS, on the other hand facing here for simplicity not shown in detail and operatively connected to the drive shaft AN drive motor of the transmission. In the in 2 illustrated transmission scheme is exemplified a torque converter in Kraftflußrichtung between the drive motor and drive shaft AN arranged. The coupled web ST VS forms the input element of the transfer gearset VS, wherein a web plate of this web ST_VS facing the main gearset HS is connected rotationally fixed to the drive input shaft AN of the transmission. The ring gear HO_VS forms the output element of the transfer gearset HS and generates a speed which is smaller than the rotational speed of the drive shaft AN and the same direction of rotation as the rotational speed of the drive shaft AN. This output speed of the transfer gearset VS can be transferred via the first and second shift elements A and B to two different input elements of the main gearset HS.

The first and second sun gear S1_HS, S2_HS of the main gearset HS rotationally connected to each other, form the first input element of the main gearset HS and are over here designed as a multi-plate clutch second switching element B with the starting element - ie the ring gear HO_VS - des Transfer gearset VS connectable. The second ring gear H2_HS of the main gearset HS forms the second input element of the main gearset HS and is over the here designed as a multi-plate clutch first switching element A also with the starting element - ie the ring gear HO_VS - des Transfer gearset VS connectable. The coupled bridge ST13_HS of the Main gearset HS forms the third input element of the main gearset HS and is on the one hand about designed here as a multi-plate clutch fifth switching element E with the Drive shaft AN connectable, on the other hand optionally also via the here exemplified as a multi-disc brake fourth switching element D on the gearbox GG determinable. The third sun gear S3_HS of the main gearset HS forms the fourth input element of the main gearset HS and is on the one hand over here designed as a multi-plate clutch sixth switching element F with the drive shaft AN connectable, on the other hand optionally also over here exemplified as a multi-disc brake third switching element C on the gearbox GG determinable. The coupled ring gear H13_HS and the second bridge ST2_HS of the main gearset HS are rotationally connected with each other, form the output element of the main gearset HS and are with the Drive shaft AB of the transmission connected.

From the structure of the main gearset HS and its kinematic coupling to the individual switching elements A to F it can be seen that in the difference to 1 in 2 in the 1 existing fixed coupling between the output elements 230 . 330 . 630 the three switching elements B, C, F and the first input element of the main gearset HS (in 1 that is, the sun gear S1_HS) is replaced by a combination of a fixed coupling between the output element 230 the clutch B and the first input element of the main gearset HS (in 2 ie the coupled sun gears S1_HS and S2_HS), from a fixed coupling between the output element 330 brake C and output element 630 the clutch F and the fourth input element of the main gearset HS (in 2 that is, the sun gear S3_HS, as well as a kinematic coupling between the first and fourth input elements of the main gearset HS via the long planet gears P13_HS of the main gearset HS. Accordingly, the lines of the first and fourth input element of the main gearset HS fall in accordance with a speed plan of the transmission according to the invention 2 together. Should be provided in a modification of the main gearset HS that said long planet gears P13_HS different from the illustration in 2 are designed as stepped planetary gears, so would be in the associated to this modification speed plan, the lines of the first and fourth input element of the modified main gearset adjacent to each other.

According to the invention form the fifth and sixth switching element E, F a manufacturing technology easily preassembled module, a common for the fifth and sixth switching element E, F plate carrier ZYLEF, each a disk set 500 . 600 for the fifth and sixth switching element E, F, and each one servo device 510 . 610 for the fifth and sixth switching element E, F for actuating the respective disk set 500 . 600 of the fifth and sixth switching element E, F comprises. Here, the common for the two clutches E, F disc carrier ZYLEF forms both the input element 520 the clutch E and the input element 620 the clutch F. As in 2 it can be seen, this assembly with the two Kupplun conditions E, F spatially seen on the main gearset HS facing side of the transfer gearset VS arranged. Depending on the geometric design, in particular of the transfer gearset VS and the disk packs 500 . 600 The clutches E, F can also be provided in another embodiment of the couplings E, F comprehensive assembly that the disk packs 500 . 600 the couplings E, F deviating from the illustration in 2 are arranged partially or even in a region radially above the transfer gearset VS, but with essential components of the clutches E, F comprehensive assembly - especially the servo devices 510 . 610 the clutches E, F - then still at least predominantly on the side facing away from the main gearset HS side of the transfer gearset VS are arranged.

As in 2 Furthermore, it can be seen that here designed as a multi-disc clutch first switching element A and also designed here as a multi-plate clutch second switching element B are arranged on the side of the transfer gearset VS, which is the assembly with the two clutches E, F, spatially seen in a range axially between Vorschaltradsatz VS and main gearset HS. In this case, the clutch A is arranged closer to the transfer gearset VS than the clutch B, the clutch A axially adjacent directly to the transfer gearset VS on the side facing the main gearset HS and the clutch B axially facing directly to the clutch A on the main gearset HS Side adjacent. The plate packs 100 . 200 The two clutches A, B are arranged by way of example on the same diameter, which allows the use of identical lamellae for these clutches A, B. An input element 120 the clutch A is exemplified as cylindrical outer disk carrier, which is connected rotationally fixed on the one hand at its vorschaltradsatznahen end with the ring gear HO_VS and on the other hand at its inner diameter in the region of his hauptradsatznahen end a suitable driving profile for receiving, for example, as externally toothed lining blades formed outer disks of the disk set 100 the clutch A has. An input element 220 the clutch B is also exemplified as a cylindrical outer disk carrier and has at its inner diameter in the region of his hauptradsatznahen end a suitable driving profile for receiving, for example, as externally toothed lining blades formed outer disks of the disk set 200 the clutch B on. At its end facing the clutch A or the transfer gearset VS is the input element 220 the clutch B with the input element 120 the clutch A rotationally connected, so is about the input element 120 the clutch A connected to the ring gear HO_VS the Vorschaltradsatzes VS. Of course, these two input elements 120 . 220 also be made in one piece. The output elements 130 . 230 Both clutches A, B are respectively formed as an inner disk carrier and have at their outer diameter in each case a suitable driving profile for receiving, for example, formed as an internally toothed steel disks inner disks of the respective disk set 100 respectively. 200 , The largely disk-shaped inner disk carrier 130 The clutch A extends in this case approximately parallel to the transfer gearset VS and is in its hub region with a second sun shaft 140 rotationally connected. This second sun wave 140 in turn extends starting from the clutch A axially in the direction of the main gearset HS, penetrates in its course both the arranged next to the clutch A clutch B and the main gearset HS centric complete, and is on the side of the main gearset HSZ with the second ring H2_HS of the Main gearset HS torsionally connected. As is known, said ring gear H2_HS forms the second input element of the main gearset HS. The likewise largely disk-shaped inner disk carrier 230 the clutch B extends approximately parallel to the inner disk carrier 130 the clutch A and is in its hub area with a first sun shaft 240 rotationally connected. This first sun wave 240 in turn, starting from the clutch B, extends axially in the direction of the main gearset HS, penetrates centrally in its axial course the third sun gear S3_HS of the main gearset HS close to the transfer gearset, thereby enclosing the second sun shaft 140 radial, and is connected to the two coupled sun gears S1_HS and S2_HS of the main gearset HS. As is known, the mentioned coupled sun gears S1_HS, S2_HS form the first input element of the main gearset HS.

In 2 for the sake of simplicity, only schematically are a servo device 110 for actuating the disk pack 100 the clutch A and a servo device 210 for actuating the disk pack 200 the clutch B. The servo 110 the clutch A is in this case axially between the transfer gearset VS and the output element 130 or inner disk carrier of the clutch A arranged and exemplified at this output element 130 or inner disk carrier of the clutch A mounted axially displaceable. When closing the clutch A actuates this servo 110 the plate set associated with it 100 axially in the direction of the main gearset HS. It makes sense to point the servo 110 also a dynamic pressure equalization in order to compensate for a rotational pressure of their always at rotational speed of the second input element of the main gearset HS, so here always with rotational speed of the ring gear H2_HS rotating pressure chamber. The servo device 210 the clutch B is exemplified here on the clutch A or the Vorschaltradsatz VS opposite side of the disk set 200 the clutch B and arranged on the output element 230 or inner disk carrier of the clutch B mounted axially displaceable. When closing the clutch B actuates this servo 210 the plate set associated with it 200 axially in the direction of the transfer gearset VS. It makes sense to point the servo 210 also a dynamic pressure compensation to compensate for a rotational pressure of their always rotating at speed of the first input element of the main gearset HS, so here always with rotational speed of the two sun gears S1_HS and S2_HS rotating pressure chamber.

As in 2 Furthermore, both the example designed here as a multi-disc brake third switching element C and the example here also designed as multi-disc brake fourth switching element D are arranged on the side of the transfer gearset VS, which is the assembly with the two clutches E, F, spatially seen in one Range axially between the clutch B and the main gearset HS. In this case, the brake D is arranged closer to the main gearset HS than the brake C. A servo device 310 for actuating a disk pack 300 the brake C and a servo device 410 for actuating a disk pack 400 the brake D are in 2 for simplicity, shown only schematically, spatially seen axially between the two plate packs 300 and 400 arranged and mounted axially displaceable in corresponding piston chambers of the transmission housing GG. By way of example, the outer disk carriers of both brakes C, D are integrated into the transmission housing GG. Of course, if necessary, the skilled person will also provide for each of the two or both brakes C, D a separate outer disk carrier or a common for both brakes C, D outer disk carrier, which is then connected as a separate component rotationally fixed to the transmission housing GG. Of course, if necessary, the person skilled in the art will also integrate the servo device associated with the respective brake with the separate outer disk carrier into the said separate outer disk carrier. The starting element 330 the brake C is formed here as a largely disk-shaped inner disk carrier, which spatially seen starting from the inner diameter of the disk set 300 the brake C extends radially inwardly and in its hub region with a third sun shaft 640 rotationally connected. This third sun wave 640 represents the mechanical connection of the output element 330 the brake C to the third sun gear S3_HS of the main gearset HS, which is close to the transfer gearset, and encloses an axial section of the web shaft 540 radial. sun wave 640 and sun gear S3_HS can also be made in one piece. The starting element 430 The brake D is also formed here as a largely disk-shaped inner disk carrier, which spatially seen starting from the inner diameter of the disk set 400 the brake D extends radially inwards up to the transfer gear set near web plate of the coupled web ST13_HS of the main gearset HS, with which it is also rotationally connected. Inner disk carrier 430 and web plate-related web plate of the web ST13_HS can also be made in one piece.

Of course, the skilled person will also modify the spatial position of the two brakes C, D within the gear housing if necessary, so that deviating from the illustration in 2 the brake C is arranged, for example, in the region of the housing wall GW and / or the brake D is arranged, for example, in a region radially above the main gearset HS.

Coming back to the assembly formed by the two clutches E, F, is in 2 It can be seen that the disk carrier ZYLEF common to the clutches E and F forms the input element for both clutches E, F and is accordingly rotationally connected to the drive shaft AN. For the clutch E, the disk carrier ZYLEF is designed as an outer disk carrier for accommodating, for example, external disks of the disk pack formed as externally toothed steel disks 500 formed of the clutch E, for the clutch F as an inner disk carrier for receiving, for example, designed as internally toothed lining disks inner disks of the disk set 600 the clutch F. Spatially seen is the disk set 600 the clutch F in a region radially above the disk pack 500 arranged the clutch E, wherein the radially inner plate pack 500 axially directly adjacent to the transfer gearset VS, in particular axially directly adjacent to the ring gear HO_VS of the transfer gearset VS is arranged. Of course, instead of the mutually arranged steel plates (without friction lining) and lining plates also unilaterally occupied with a friction lining steel plates can be used, in which case an externally toothed occupied steel plate and an internally toothed occupied steel plate must be mutually assembled to form a plate pack. Of course, instead of the proposed steel plates also lamellae made of carbon or carbon fibers or other suitable composite materials may be used. Geometrically, said plate carrier ZYLEF is designed essentially in the form of a pot open in the direction of the transfer gearset VS. At the inside diameter of a stepped cylindrical section 521 of the plate carrier ZYLEF are the outer plates of the plate pack 500 the clutch E arranged. An at least largely disk-shaped section (pot bottom) 522 of the plate carrier ZYLEF joins the mentioned cylindrical section 521 of the plate carrier ZYLEF and extends from the off-gear set distal end of the cylindrical portion 521 radially inward. At the inner diameter of said pot bottom ( 522 ) of the plate carrier ZYLEF is followed by a hub of the plate carrier ZYLEF. Starting from the inner diameter of said pot bottom ( 522 ) extends to the clutch E attributable first hub portion 523 of the disk carrier ZYLEF axially in the direction of the transfer gearset VS. This first hub section 523 is at its vorratsradsatznahen end with a main gearset distant web plate of the coupled web ST VS of the transfer gearset VS rotationally connected, wherein the hauptradsatznahe web plate of this web ST VS is rotationally connected to the drive shaft AN. One of the clutch F assignable second hub portion 623 of the disk carrier ZYLEF extends from the inner diameter of the disk-shaped portion 522 or cup bottom of the plate carrier ZYLEF axially in opposite direction to the transfer gearset VS direction or axially in the direction of the housing wall GW. The hub of the plate carrier ZYLEF with its hub sections 523 and 623 on the gearbox fixed hub GN, to which the sun gear SO_VS of the transfer gearset VS is fixed rotatably mounted. The outer diameter of the cylindrical section 521 of the plate carrier ZYLEF is with 621 indicates, as an indication that this section is also assigned to the clutch F. At this outer diameter is namely a driving profile for receiving the inner disk of the disk set 600 provided the clutch F.

The servo device 510 the clutch E to operate their disc pack 500 includes a pressure chamber 511 , a pressure compensation room 512 , a piston 514 , a reset element 513 and a baffle plate 515 and is radially above the first hub cut 523 of the plate carrier ZYLEF completely disposed within a cylinder space, which is defined by the plate carrier ZYLEF, in particular by its cylindrical portion 521 is formed. The piston 514 is mounted axially displaceable on this plate carrier ZYLEF. Accordingly, the servo device rotates 510 constantly at speed of the drive shaft AN. To compensate for the rotary pressure of the rotating pressure chamber 511 the servo device 510 is a dynamic pressure equalization with the pressureless with lubricant fillable pressure compensation chamber 512 provided, this pressure equalization space 512 is arranged closer to the main gearset HS than said pressure chamber 511 , This is the pressure chamber 511 through a lateral surface of the plate carrier ZYLEF and the piston 514 educated. The pressure compensation room 512 is formed by the piston 514 and the baffle plate 515 , which axially on the hub portion 523 of the plate carrier ZYLEF is fixed and opposite the piston 515 axially displaceable lubricant seal is sealed. The piston 514 is about the example here designed as a plate spring return element 513 axially against the hub portion 523 of the plate carrier ZYLEF biased. When loading the pressure chamber 511 with pressure means for closing the clutch E, the piston moves 514 axially in the direction of the transfer gearset VS or axially in the direction of the main gearset HS and actuates the disk pack assigned to it 500 against the spring force of the return element 513 ,

Spatially seen is the servo device 510 the clutch E closer to main and transfer gearset HS, VS arranged as the servo device 610 the clutch F. Here is this servo device 610 spatially seen at least predominantly in a region radially above the second hub portion 623 arranged the plate carrier ZYLEF and also axially slidably mounted on the plate carrier ZYLEF. The servo also rotates accordingly 610 constantly at speed of the drive shaft AN. The servo device 610 the clutch F comprises a pressure chamber 611 , a pressure compensation room 612 , a sectionally meander-shaped piston 614 , a reset element 613 , a cylindrical baffle plate 615 and a cup-shaped support disk 618 , To compensate for the rotary pressure of the rotating pressure chamber 611 the servo device 610 is a dynamic pressure equalization with the pressure equalization chamber 612 intended. For this purpose, the cylindrical baffle plate extends 615 on a defined diameter above the hub angle 623 starting from the disk-shaped section 522 of the disk carrier ZYLEF axially toward the housing wall GW and is to the axially adjacent piston 614 sealed axially displaceable lubricant seal. Together with the radially below the baffle plate 615 located and the housing wall GW facing lateral surface portion of the disk carrier ZYLEF and the radially below the baffle plate 615 located and the Vorschaltradsatz VZ facing lateral surface portion of the piston 614 forms this baffle plate 615 the said pressure equalization space 612 , In the example shown are baffle plate 615 and disk carrier ZYLEF example embodied in one piece, but can of course also be designed as separate components.

The pressure compensation room 612 the servo device 610 the clutch F and the pressure chamber 511 the servo device 510 The clutch E are thus arranged directly adjacent to each other and separated from each other only by a lateral surface of the common for the clutches E and F disc carrier ZYLEF. On the pressure room 511 or the transfer gearset VS side facing away from the Pressure equalization chamber 612 is the pressure room 611 the servo device 610 arranged. This pressure chamber is formed 611 through the piston 615 and the support disk 618 and an axial portion of the hub 623 , For this purpose, the support disk 618 fluid-tight at the hub 623 attached. Radially above the section of the hub 623 that the pressure room 611 forms, extends a cylindrical portion of this cup-shaped support disk 618 axially in the direction of the pressure chamber 511 or axially in the direction of the transfer gearset VS and is against a corresponding portion of the piston 614 sealed pressure-tight axially movable. In its werteren geometric course, the piston extends 614 at least largely along the outer contour of support disk 618 and upper region of the disk carrier ZYLEF radially outward and axially in the direction of the main gearset HS up to the main wheel set remote side of its associated disk set 600 the clutch F. Axial biased is the piston 614 through the return element 613 exemplified here as an axially between the disc-shaped section 622 of the plate carrier ZYLEF and the piston 614 arranged coil spring assembly of annularly arranged, kinematically connected in parallel coil springs is formed. When loading the pressure chamber 611 with pressure medium to close the clutch F, the piston moves 614 axially in the direction of the transfer gearset VS or axially in the direction of the main gearset HS and actuates the disk pack assigned to it 600 against the spring force of the return element 613 ,

Due to the mounting of the plate carrier ZYLEF to the gearbox fixed hub GN results in a structurally comparatively simple pressure and lubricant supply to both clutches E, F via corresponding channels or holes that partially within said gearbox fixed hub GN and partially within the hub of the plate carrier ZYLEF run. A pressure medium supply to the pressure chamber 51i the servo device 510 the clutch E is with 516 denotes a lubricant supply to the pressure compensation chamber 512 the servo device 510 the clutch E with 517 , a pressure medium supply to the pressure chamber 611 the servo device 610 the clutch F with 616 , and a lubricant supply to the pressure compensation chamber 612 the servo device 610 the clutch F with 617 ,

The starting element 530 the clutch E is formed as an inner disk carrier, which is based on the disk set 500 the clutch E axially adjacent to the servo device 510 The clutch E initially extends axially in the direction of the transfer gearset VS and just ahead of the ring gear HO_VS of this transfer gearset radially outward until just above the outer diameter of said ring gear HO_VS or until just above the outer diameter of the input element connected to said ring gear HO_VS 120 the clutch A. In the area of its outer diameter is the inner disk carrier 530 the clutch E connected rotationally fixed with a cylindrical connecting element ZYL. This cylindrical connecting element ZYL is designed as a pot open in the direction of the clutch E, which completely encloses the transfer gearset VS, the clutch A axially adjacent to the transfer gearset VS, and the clutch B axially adjacent to the clutch A. A disc-shaped pot bottom of this connecting element ZYL here borders axially on the servo device 210 the clutch B and is in the range of its inner diameter or its hub with the web shaft 540 rotationally connected. The bridge wave 540 in turn extends axially in the direction of the main gearset HS up to a region between the third sun gear S3_HS close to the transfer gearset and the spatially middle first sun gear S1_HS of the main gearset HS and penetrates the third sun gear S3_HS of the main gearset HS and is connected rotationally fixed to the coupled web ST13_HS of the main gearset HS , In this respect, said cylindrical connection element ZYL can also formally correspond to the output element 530 be assigned to the clutch E.

The starting element 630 The coupling F is designed as an outer disk carrier, geometrically in the form of a pot which opens in the direction of the clutch F or housing wall GW and which radially surrounds the previously described cylindrical connecting element ZYL. A disc-shaped pot bottom of this output element 630 or outer disk carrier of the clutch F extends spatially axially between the pot bottom of said connecting element ZYL and the disk-shaped output element 330 or inner disk carrier of the brake C in the radial direction and is in its hub region with the third sun shaft 640 rotationally connected, with the also the output element 330 or the inner disk carrier of the brake C and the third sun gear S3_HS of the main gearset is rotationally connected. At the outer diameter of the pot bottom of the output element 630 or outer disk carrier of the clutch F is followed by a cylindrical portion of the output element 630 or outer disk carrier of the clutch F and extends axially in the direction of the housing wall GW to over the disk set 600 the clutch F away. In the region of its housing wall-side end, the said cylindrical section of the output element or outer disk carrier 630 at its inner diameter a suitable driving profile on for receiving the externally toothed lamellae of the disk set 600 the clutch F.

Based 3 Now, a second exemplary transmission scheme according to the present invention will be explained based on the above 2 described in detail first inventive transmission scheme, but with a too 2 alternative structural design of the assembly with the fifth and sixth switching element E, F. The main difference between the second inventive transmission scheme according to 3 and the first inventive transmission scheme according to 2 is the spatial arrangement of the disk packs 500 . 600 the two brakes E, F relative to each other. According to 3 is the disk pack 500 the clutch E now radially over the disk pack 600 arranged the clutch F. According to this arrangement, the spatial position of the servo devices 510 . 610 the two clutches E, F adapted, wherein the servo device 610 the clutch F is now closer to the transfer gearset VS is arranged as the servo device 510 the clutch E. In direct comparison between 3 and the underlying 2 is easily seen that the entire assembly of the two clutches E, F component side are identical, with only the part names have changed. All components of this assembly, in 2 Namely assigned to the clutch E, are in 3 now assigned to the clutch F. Accordingly, all components of this assembly, which are in 2 Namely, the clutch F are assigned, in 3 now assigned to the clutch E. In this respect, the further description of the assembly with the common for both clutches E, F disc carrier ZYLEF, as well as the servo devices 510 . 610 and the disk packs 500 . 600 both clutches E, F are limited to the reference of the correspondingly adapted reference numerals.

As according to 3 the disk pack 500 the clutch E unlike 2 radially above the disk pack 600 the clutch F is arranged, is now also the now formed as an inner disk carrier output element 630 the clutch F within the output element 530 the clutch E arranged. In this case, the said output element surrounds 630 the clutch F the transfer gearset VS and the two clutches A and B in the axial direction radially and is axially adjacent to the output member 230 the clutch B against rotation with the first sun shaft 240 connected. This first sun wave 240 In turn, in its axial course, the third sun gear S3_HS of the main gearset HS, which is close to the transfer gearset, passes through and encloses the second sun shaft 140 showing the mechanical connection between the output element 130 the clutch A and the formed by the ring gear H2_HS second input element of the main gearset HS, radially and is rotationally connected to the two coupled sun gears S1_HS and S2_HS of the main gearset. The now formed as an outer disk carrier output element 530 the clutch E engages around the output element 630 or the inner disk carrier of the clutch F in the axial direction radially and is on the web shaft 540 connected to the coupled web ST13_HS of the main gearset HS. This bridge shaft passes through 540 In its axial course, the third sun gear S3_HS of the main gearset HS close to the transfer gearset, thereby enclosing the first sun shaft 240 radial. In the area axially between the third sun gear S3_HS close to the transfer gearset and the spatially seen first sun gear S1_HS of the main gearset HS, the ridge wave is 540 connected in a rotationally fixed manner to a web plate of the coupled web ST13_HS of the main gearset HS close to the transfer gearset, wherein said web plate axially engages axially between the two sun gears S3_HS and S1_HS. The starting element 330 the brake C is now rotationally connected solely to the third sun gear S3_HS of the main gearset HS.

From the in 3 shown construction of the main gearset HS and its kinematic coupling to the individual switching elements A to F can be seen that, in contrast to 1 in 3 in the 1 existing fixed coupling between the output elements 230 . 330 . 630 the three switching elements B, C, F and the first input element of the main gearset HS (in 1 that is, the sun gear S1_HS) is replaced by a combination of a fixed coupling between the output element 230 the clutch B and output element 630 the clutch F and the first input element of the main gearset HS (in 3 ie the coupled sun gears S1_HS and S2_HS), from a fixed coupling between the output element 330 the brake C and the fourth input element of the main gearset HS (in 3 that is, the sun gear S3_HS, as well as a kinematic coupling between the first and fourth input elements of the main gearset HS via the long planet gears P13_HS of the main gearset HS. Accordingly, the lines of the first and fourth input element of the main gearset HS fall in accordance with a speed plan of the transmission according to the invention 3 together. Should be provided in a modification of the main gearset HS that said long planet gears P13_HS different from the illustration in 3 are designed as stepped planetary gears, so would be in the associated to this modification speed plan, the lines of the first and fourth input element of the modified main gearset adjacent to each other.

Based 4 Now, a third exemplary transmission scheme according to the present invention will be explained based on the above 2 described first inventive transmission schema, but with one too 2 alternative spatial arrangement of the assembly with the fifth and sixth switching element E, F and an alternative spatial arrangement of the third and fourth switching element C, D within the transmission.

As in the underlying prior art, both the third switching element C and the fourth switching element D is designed as a brake, both by way of example in the form of a multi-disc brake. Out 4 is easily seen that the "new" arrangement of the two brakes C, D now on the side of the main gearset HS, which is the transfer gearset VS, in conjunction with the coaxial arrangement of the transfer gearset VS and main gearset HS an arrangement of axially parallel or angled mutually arranged drive and output shaft AN, AB of the transmission allows, an arrangement that is necessary, for example, for a motor vehicle with front-wheel drive and arranged transversely or longitudinally to the direction of travel drive motor. For simplicity, in 4 a spur gear stage or bevel gear stage to be provided as needed for connecting the output element of the main gearset HS to the transmission output is not shown in greater detail. In 4 also not shown in detail for simplification is an operatively connected to the drive shaft AN drive motor of the transmission, which is arranged here by way of example on the side facing away from the main gearset HS side of the transfer gearset VS. Accordingly, the drive shaft AN also penetrates here practically the entire transmission in the axial direction, at least all wheelsets VS, HS. In this respect, it requires no special design effort to order the drive motor on the other side of the transmission, so on the side of the main gearset HS away from the transfer gearset.

The in 4 provided main gearset HS is as in 2 designed as a "two-track unit reduced two-track five-shaft planetary gear" and arranged coaxially next to the designed as a simple plus planetary gearset VS and coaxial with the drive shaft AN. The main gearset HS has four non-interconnected input elements and an output element and is formed from two mutually coupled individual planetary gear sets, wherein one of these two individual planetary gear sets has a "split sun gear". Accordingly, the main gearset HS includes as in 2 three sun gears S1_HS, S2_HS, S3_HS, a coupled first ring gear H13_HS, a second ring gear H2_HS, a coupled first web ST13_HS with long planetary gears P13_HS rotatably mounted thereon, and a second web ST2_HS with short planetary gears P2_HS rotatably mounted thereon. According to the nomenclature of the connection of the input elements of the main gearset HS to the various switching elements A to F, the second of the two individual planetary gear sets of the main gearset HS comprises the second sun gear S2_HS, the second ring gear H2_HS and the second web ST2_HS with the short planetary gears P2_HS rotatably mounted thereon but is different from 2 now arranged vorschaltradsatznah. The first individual planetary gear set of the main gearset HS comprises the first and third sun gear S1_HS, S3_HS, the coupled ring gear H13_HS and the coupled web ST13_HS with the long planetary gears P13_HS rotatably mounted thereon and is in contrast to 2 arranged according to now vorschaltradsatzfern. The short planet gears P2_HS mesh with the second ring gear H2_HS and the second sun gear S2_HS, the long planet gears P13_HS with the coupled ring gear H13_HS and the first and third sun gear S1_HS, S3_HS. The long planetary gears P13_HS are like in 2 For example, not designed as a stepped planet, the two sun gears S1_HS and S3_HS of the main gearset HS thus have identical numbers of teeth here. Spatially, the first sun gear S1_HS of the main gearset HS is arranged axially between the second and third sun gear S2_HS, S3_HS of the main gearset HS, this second sun gear S2_HS being arranged closer to the transfer gearset VS than this third sun gear S3_HS.

As in 2 are the first and second sun S1_HS, S2_HS firmly connected to each other and form the first input element of the main gearset HS, which with the output elements 230 . 630 the clutches B and F is rotationally fixed on the side of the main gearset HS close to the transfer gearset. The second ring gear H2_HS forms the second input element of the main gearset HS and is connected to the output element 130 the clutch A rotationally connected. The coupled web ST13_HS forms the third input element of the main gearset HS and is - in accordance with the spatial position of the brake D - on the side of the main gearset HS remote from the transfer gearset HS rotationally fixed to the output element 430 connected to the brake D and - according to the spatial position of the clutch E - via an axially between the first and third sun S1_HS, S3_HS extending radial penetration with the output element 530 the clutch E connected. The third sun gear S3_HS forms the fourth input element of the main gearset HS and is - in accordance with the spatial position of the brake C - on the side of the main gearset HS remote from the transfer gearset VS rotationally fixed to the output element 330 the brake C connected. The coupled ring gear H13_HS and the second web ST2_HS are firmly connected to one another and form the output element of the main gearset HS connected to the output shaft AB of the gearbox. In a speed plan of the automatic transmission according to 4 fall the lines of the first and fourth input element of the main gearset HS according to the described component-side and kinematic coupling whose three sun gears S1_HS, S2_HS, S3_HS together. In accordance with the kinematic coupling of the two brakes C, D to the main gearset HS, the brake D is arranged closer to the main gearset HS than the brake C, the brake D being different from 2 now also closer to the transfer gearset VS is arranged as the brake C.

According to the invention form the clutches E and F a manufacturing technology easily preassembled assembly, which is now arranged in a range axially between the transfer gearset VS and main gearset HS and axially adjacent to the transfer gearset VS. In this case, this assembly includes both here exemplified as outer disk carrier input elements 520 . 620 the clutches E and F and for both clutches E, F depending on a disk set 500 respectively. 600 and one servo each 510 respectively. 610 for actuating the respectively assigned disk pack 500 respectively. 600 ,

In the in 4 illustrated embodiment, the clutch F is spatially arranged radially above the clutch E, in particular the disk set 600 the clutch F spatially seen radially above the disk pack 500 the clutch E is arranged. The input element or the outer disk carrier 520 the clutch E is formed geometrically in the form of a direction of the main gearset HS open pot whose hub is rotatably connected to the drive shaft AN, in the example shown even forms a common with the drive shaft AN component. The servo device 510 the clutch E is disposed entirely within a cylinder space passing through the outer disk carrier 520 the clutch E is formed, and on this outer disk carrier 520 mounted axially displaceable. Accordingly, the servo device rotates 510 constantly at speed of the drive shaft AN. To compensate for the rotary pressure of the rotating pressure chamber 511 the servo device 510 is a dynamic pressure equalization with the pressure equalization chamber 512 provided, this pressure chamber 511 is arranged closer to the transfer gearset VS than said pressure compensation chamber 512 ,

The input element or the outer disk carrier 620 the clutch F is also geometrically in the form of a direction of the main gearset HS open pot formed, the hub with the input member or outer disk carrier 520 the clutch E is connected to the outer diameter rotationally fixed. The input element 620 the clutch F is thus on the input element 520 the clutch E connected to the drive shaft AN. The servo device 610 the clutch F is completely disposed within a cylinder space, which by the outer disc carrier ( 620 ) of the clutch F is formed, and on this outer disc carrier ( 620 ) mounted axially displaceable. Accordingly, the servo device rotates 610 constantly at speed of the drive shaft AN. To compensate for the rotary pressure of the rotating pressure chamber 611 the servo device 610 is a dynamic pressure equalization with the pressure equalization chamber 612 provided, this pressure chamber 611 is arranged closer to the transfer gearset VS than said pressure compensation chamber 612 ,

Spatially seen is the servo device 610 the (radially outer) clutch F in a region radially above the servo device 510 the (radially inner) clutch E arranged. Accordingly, the pressure chamber 611 the (radially outer) servo 610 the clutch F at least approximately radially above the pressure chamber 511 the (radially inner) servo 510 the clutch E and the pressure compensation chamber 612 the (radially outer) servo 610 the clutch F at least approximately radially above the pressure compensation chamber 512 the (radially inner) servo 510 the clutch E arranged. A pressure medium supply to the pressure chamber 511 and a lubricant supply to the pressure-free fillable pressure compensation chamber 512 the servo device 510 the clutch E runs in sections within the hub of the input element (outer disk carrier) 520 the clutch E and sections within the drive shaft AN. A pressure medium supply to the pressure chamber 611 servo 610 the (radially outer) clutch F also runs in sections within the (outer disk carrier) 520 the (radially inner) clutch E and sections within the drive shaft AN. The pressure compensation room 612 the servo device 610 The clutch F is here for example directly over the pressure compensation chamber 512 the servo device 510 the clutch E pressureless filled with lubricant. To close the clutch E is the pressure chamber 511 the servo device 510 filled with pressure medium, which then assigned to her plate pack 500 the clutch E is actuated axially in the direction of the main gearset HS. To close the clutch F is the pressure chamber 611 the servo device 610 filled with pressure medium, which then assigned to her plate pack 600 the clutch F is actuated axially in the direction of the main gearset HS.

The output elements 530 . 630 the two clutches E, F are both formed in the illustrated embodiment as an inner disk carrier. The inner disc carrier 530 the clutch E extends from the disk pack 500 the clutch E axially adjacent to the servo device 510 the clutch E radially inward and is centered with the web shaft 540 torsionally connected. This bridge wave 540 extends axially in the direction of the main gearset HS up to the web plate of the transfer gearset distant (coupled) first web ST13_HS of the main gearset HS, passes through the second and first sun gear S2_HS, S1_HS of the main gearset HS centric in the axial direction, and is in a range axially between the third and the first sun gear S3_HS, S1_HS of the main gearset HS are rotationally connected to said web plate of the web ST13_HS. Of course, the mentioned web plate of the web ST13_HS and the web shaft 540 also be made in one piece. The inner disc carrier 630 the clutch F extends from the disk pack 600 the clutch F sections axially adjacent to the inner disc carrier 530 the clutch E radially inward to a diameter just above the web shaft 540 and is in this hub area with a hub of the output element 230 the clutch B and the sun's shaft 140 connected rotationally fixed to the two sun gears S2_HS and S1_HS of the main gearset HS. The bridge wave 540 thus runs centrally within this hub of the output element 630 the clutch F or this hub of the output element 230 the clutch B and centric within the sun shaft 140 , If necessary, the person skilled in the art will make the connection between the hubs of the two output elements 230 . 630 also about the sun wave 140 or even the two sun gears S2_HS, S1_HS in one piece.

In the in 4 illustrated embodiment, the disk packs 200 and 100 the two clutches B and A spatially arranged axially next to each other on at least similar diameter in an area at least partially radially above the assembly formed from the two clutches E and F. The starting element 230 The clutch B engages around the assembly formed from the two clutches E, F radially in the axial direction, wherein the cylindrical portion 231 this output element 230 at least substantially radially above the outer diameter of the input element (outer disk carrier) 620 extends the clutch F while the clutch F completely overlaps, and wherein the disc-shaped portion 232 this output element 230 at least largely parallel to the output element (inner disk carrier) 630 the clutch F extends. A for simplicity only schematically illustrated servo device 210 the clutch B to operate the disk pack 200 the clutch B may, for example, as in 4 indicated to be arranged at least predominantly on the main gearset remote side of the transfer gearset VS, always rotate at rotational speed of the drive shaft AN and its associated disk set 200 when closing the clutch B actuate axially in the direction of the main gearset HS. A simplification also shown only schematically servo device 110 the clutch A for actuating the disk pack 100 For example, as shown in FIG 4 indicated axially between the output element 230 the clutch B and the main gearset HS on the main gearset HS facing side of the disk set 100 be arranged, always rotate at the speed of the first input element of the main gearset HS formed here by the coupled sun gears S1_HS, S2_HS, and the disk pack associated therewith 100 when closing the clutch A, actuate it axially in the direction of the transfer gearset VS.

Based 5 Now, a fourth exemplary transmission scheme according to the present invention will be explained based on the above 4 described in detail third inventive transmission scheme, but with a too 4 alternative structural design of the construction group with the fifth and sixth switching element E, F. As in 4 form the clutches E and F a manufacturing technology easily preassembled module, comprising both here exemplified as outer disk carrier input element 520 . 620 the clutches E and F, the servos 510 . 610 Both clutches E and F, and the disk packs 500 . 600 both clutches E and F. In contrast to 4 However, now the clutch E is spatially arranged radially above the clutch F, in particular the disk set 500 the clutch E spatially seen radially above the disk set 600 the clutch F is arranged.

The input element or the outer disk carrier 620 the clutch F is geometrically designed in the form of a direction of the main gearset HS open pot whose hub is rotatably connected to the drive shaft AN, in the example shown even forms a common with the drive shaft AN component. The servo device 610 the clutch F is completely disposed within a cylinder space passing through the outer disc carrier 620 the clutch F is formed, and on this outer disk carrier 620 mounted axially displaceable. Accordingly, the servo device rotates 610 constantly at speed of the drive shaft AN. To compensate for the rotary pressure of the rotating pressure chamber 611 the servo device 610 is a dynamic pressure equalization with the pressure equalization chamber 612 provided, this Durckraum 611 is arranged closer to the transfer gearset VS than said pressure compensation chamber 612 ,

The input element or the outer disk carrier 520 The clutch E is also formed geometrically in the form of a direction of the main gearset HS open pot, the hub with the input member or outer disk carrier 620 of the Clutch F is connected to the outer diameter rotationally fixed. The input element 520 the clutch E is therefore on the input element 620 the clutch F connected to the drive shaft AN.

The servo device 510 the clutch E is disposed entirely within a cylinder space passing through the outer disk carrier 520 the clutch E is formed, and on this outer disk carrier 520 mounted axially displaceable. Accordingly, the servo device rotates 510 constantly at speed of the drive shaft AN. To compensate for the rotary pressure of the rotating pressure chamber 511 the servo device 510 is a dynamic pressure equalization with the pressure equalization chamber 512 provided, this Drurckraum 511 is arranged closer to the transfer gearset VS than said pressure compensation chamber 512 ,

Spatially seen is the servo device 510 the (radially outer) clutch E in a region radially above the servo device 610 arranged the (radially inner) clutch F: Accordingly, the pressure chamber 511 the (radially outer) servo 510 the clutch E at least approximately radially above the pressure chamber 611 the (radially inner) servo 610 the clutch F and the pressure compensation chamber 512 the (radially outer) servo 510 the clutch E at least approximately radially above the pressure equalization space 612 the (radially inner) servo 610 arranged the clutch F. A pressure medium supply to the pressure chamber 611 and a lubricant supply to the pressure-free fillable pressure compensation chamber 612 the servo device 610 the clutch F extends in sections within the hub of the input element (outer disk carrier) 620 the clutch F and sections within the drive shaft AN. A pressure medium supply to the pressure chamber 511 servo 510 the (radially outer) clutch E also runs in sections within the (outer disk carrier) 620 the (radially inner) clutch F and sections within the drive shaft AN. The pressure compensation room 512 the servo device 510 the clutch E is here for example directly over the pressure compensation chamber 612 the servo device 610 the clutch F pressureless filled with lubricant. To close the clutch E is the pressure chamber 511 the servo device 510 filled with pressure medium, which then assigned to her plate pack 500 the clutch E is actuated axially in the direction of the main gearset HS. To close the clutch F is the pressure chamber 611 the servo device 610 filled with pressure medium, which then assigned to her plate pack 600 the clutch F is actuated axially in the direction of the main gearset HS.

According to the kinematic coupling between the output elements 230 . 530 . 630 of the clutches B, E, F and the three sun gears S1_HS, S2_HS, S3_HS of the main gearset HS is the said second sun gear S2_HS as in FIG 8th arranged in front of the transfer gearset and the first sun gear S1_HS axially between the second and third sun gear S1_HS, S3_HS. In contrast to 8th is formed by the sun gears S1_HS and S2_HS firmly formed first input element of the main gearset HS only with the output element 230 connected to the clutch B, however, is formed by the third sun gear S3_HS fourth input element of the main gearset HS now both with the output element 330 the brake C as well as with the output element 630 the clutch F connected. Of course, these can be over the short sun wave here 140 If necessary, the sun gears S2_HS and S3_HS connected to one another can also be made in one piece.

The output elements 530 . 630 of the two clutches E, F are in the in 5 illustrated embodiment, both formed as an inner disk carrier. The inner disc carrier 630 the clutch F extends from the disk pack 600 the clutch F axially adjacent to the servo device 610 the clutch F radially inward and is centered with a third sun shaft 640 rotationally connected. This third sun wave 640 extends axially in the direction of the main gearset HS to at least the third planetary gear S3_HS far away from the transfer gearset, at least passes through the second sun gear S2_HS and the (spatially seen middle) first sun gear S1_HS of the main gearset HS in the axial direction and is centered with this third sun gear S3_HS rotationally connected. In principle, the third sun wave passes through 640 also this third sun S3_HS centric, since the initial element 330 the brake C on the side of the main gearset HS remote from the transfer gearset with this third sun gear S3_HS or precisely with this third sun shaft 640 twisted test is connected. The inner disc carrier 530 the clutch E extends from the disk pack 500 the clutch E sections axially adjacent to the inner disc carrier 630 the clutch F radially inward to a diameter just above the third sun shaft 640 and is in this hub area with the bridge shaft 540 rotationally connected. This bridge wave 540 again encloses the third sun wave 640 radially, extends axially in the direction of the main gearset HS up to the web plate of the transfer gearset distant coupled web ST13_HS of the main gearset HS, also passes through the second and first sun gear S2_HS, S1_HS of the main gearset HS in the axial direction, and is in an area axially between the first and third sun gear S1_HS, S3_HS of the main gearset HS are rotationally connected to said web plate of the coupled web ST13_HS. Selbstver Of course, the above-mentioned web plate of the bridge ST13_HS and the bridge shaft 540 also be made in one piece.

In the in 5 illustrated embodiment, the disk packs 200 and 100 the two clutches B and A spatially arranged axially next to each other on at least similar diameter in an area at least partially radially above the assembly formed from the two clutches E and F. The starting element 230 The clutch B engages around the assembly formed from the two clutches E, F radially in the axial direction, wherein the cylindrical portion 231 this output element 230 at least substantially radially above the outer diameter of the input element (outer disk carrier) 520 extends the clutch E while the clutch E completely overlaps, and wherein the disc-shaped portion 232 this output element 230 at least largely parallel to the output element (inner disk carrier) 530 the clutch E extends radially inwardly to a diameter just above the web shaft 540 , In its hub area is the starting element 230 the clutch B with the second sun gear S2_HS of the main gearset HS close to the transfer gearset and via a sun shaft 140 also rotationally fixed to the (spatially seen in the middle) first sun S1_HS the main gearset HS. The bridge wave 540 thus runs centrally within this hub of the output element 230 the clutch E and centric within the sun's shaft 140 ,

Otherwise corresponds to in 5 illustrated fourth component assembly according to the invention substantially already in 4 illustrated third component assembly according to the invention.

Based 6 Now, a fifth exemplary transmission scheme according to the present invention is explained, again based on the 4 described third transmission scheme according to the invention, but with one to 4 alternative spatial arrangement of the assembly with the fifth and sixth switching element E, F within the transmission. As before, the two clutches E and F form a production technology easily preassembled module, the common for both clutches E and F plate carrier ZYLEF, the servo devices 510 . 610 Both clutches E and F, and the disk packs 500 . 600 includes both clutches E and F. In contrast to 4 this assembly consisting of the clutches E, F is now arranged on the side of the main gearset HS facing away from the transfer gearset VS. The planetary gearset of the main gearset HS with the divided sun gear (ie the two sun gears S1_HS and S2_HS) is facing the assembly of the clutches E and F, the sun gear S3_HS of the main gearset HS axially adjacent to said assembly. Accordingly, the other simple planetary gear set of the main gearset HS with its sun gear S2_HS faces the transfer gearset VS.

The common for the clutches E and F plate carrier ZYLEF forms for both clutches E, F whose input element and is correspondingly rotationally connected to the drive shaft AN. For the clutch E, the disk carrier ZYLEF is used as outer disk carrier for mounting the outer disks of the disk pack 500 formed of the clutch E, for the clutch F as an inner disk carrier for receiving inner disks of the disk set 600 the clutch F. Spatially seen is the disk set 600 the clutch F in a region radially above the disk pack 500 the clutch E arranged. Geometrically, said plate carrier ZYLEF is essentially designed in the form of a pot open in the direction of the main gearset HS, with a stepped cylindrical section 521 , at the inner diameter of the outer disk of the disk set 500 the clutch E are arranged, with an at least largely disc-shaped portion (pot bottom) 522 extending from the main gear set distal end of said cylindrical portion 521 extends radially inwardly, with a clutch E to be assigned first hub portion 523 starting from the inside diameter of said pot bottom ( 522 ) extends axially in the direction of the main gearset HS and is connected at its hauptradsatznahen end to the drive shaft AN, as well as with a clutch F assignable second hub portion 623 starting from the inside diameter of said pot bottom ( 522 ) extends axially in opposite direction to the main gearset HS and is rotatably mounted at its hauptradsatzfernen end to a rotationally fixed to the transmission housing GG connected housing cover GD. The outer diameter of the cylindrical section from 521 is with 621 indicates, as an indication that this section is also assigned to the clutch F. At this outer diameter is namely the driving profile for receiving the inner disk of the disk set 600 provided the clutch F.

The servo device 510 the clutch E to operate their disc pack 500 includes a pressure chamber 511 , a pressure compensation room 512 , a piston 514 , a reset element 513 and a baffle plate 515 and is radially above the first hub cut 523 of the plate carrier ZYLEF completely disposed within a cylinder space, which is defined by the plate carrier ZYLEF, in particular by its cylindrical portion 521 is formed. The piston 514 is mounted axially displaceable on this plate carrier ZYLEF. Entspre The servo then rotates 510 constantly at speed of the drive shaft AN. To compensate for the rotary pressure of the rotating pressure chamber 511 the servo device 510 is a dynamic pressure equalization with the pressureless with lubricant fillable pressure compensation chamber 512 provided, this pressure equalization space 512 is arranged closer to the main gearset HS than said pressure chamber 511 , This is the pressure chamber 511 through a lateral surface of the plate carrier ZYLEF and the piston 514 educated. The pressure compensation room 512 is formed by the piston 514 and the baffle plate 515 , which axially on the hub portion 523 of the plate carrier ZYLEF is fixed and opposite the piston 515 axially displaceable lubricant seal is sealed. The piston 514 is about the example here designed as a plate spring return element 513 axially against the hub portion 523 of the plate carrier ZYLEF biased. When loading the pressure chamber 511 with pressure means for closing the clutch E, the piston moves 514 axially in the direction of the main gearset HS and actuates the disk set associated with it 500 against the spring force of the return element 513 ,

Spatially seen is the servo device 510 the clutch E closer to master and main gearset VS, HS arranged as the servo device 610 the clutch F. Here is this servo device 610 spatially seen at least predominantly in a region radially above the second hub portion 623 arranged the plate carrier ZYLEF and also axially slidably mounted on the plate carrier ZYLEF. The servo also rotates accordingly 610 constantly at speed of the drive shaft AN. The servo device 610 the clutch F comprises a pressure chamber 611 , a pressure compensation room 612 , a sectionally meander-shaped piston 614 , a reset element 613 , a cylindrical baffle plate 615 and a cup-shaped support disk 618 , To compensate for the rotary pressure of the rotating pressure chamber 611 the servo device 610 is a dynamic pressure equalization with the pressure equalization chamber 612 intended. For this purpose, the cylindrical baffle plate 615 on a defined diameter lubricant seal on the disc-shaped section 522 the disk carrier ZYLEF attached (welded in the example shown), to the axially adjacent piston 614 sealed axially displaceable lubricant seal and forms together with the radially below the baffle plate 615 located lateral surface 621 of the disk carrier ZYLEF and the radially below the baffle plate 615 located lateral surface of the piston 614 the said pressure equalization space 612 , The pressure compensation room 612 the servo device 610 the clutch F and the pressure chamber 511 the servo device 510 The clutch E are thus arranged directly adjacent to each other and separated from each other only by a lateral surface of the common for the clutches E and F disc carrier ZYLEF. On the main gearset HS and the pressure chamber 511 opposite side of the pressure compensation chamber 612 is the pressure room 611 the servo device 610 arranged. This pressure chamber is formed 611 through the piston 615 and the support disk 618 and an axial portion of the hub 623 , For this purpose, the support disk 618 fluid-tight at the hub 623 attached. Radially above the section of the hub 623 that the pressure room 612 forms, extends a cylindrical portion of this cup-shaped support disk 618 axially in the direction of the main gearset HS (or axially in the direction of the pressure chamber 511 ) and is against a corresponding portion of the piston 614 sealed pressure-tight axially movable. In its further geometric course, the piston extends 614 at least largely along the outer contour of support disk 618 and upper region of the disk carrier ZYLEF radially outward and axially in the direction of the main gearset HS up to the main wheel set remote side of its associated disk set 600 the clutch F. Axial biased is the piston 614 through the return element 613 in that here by way of example as an axially between the disc-shaped plate carrier section 621 and the piston 614 arranged spiral spring packet is formed. When loading the pressure chamber 611 with pressure medium to close the clutch F, the piston moves 614 axially in the direction of the main gearset HS and actuates the disk set associated with it 600 against the spring force of the return element 613 ,

Due to the mounting of the disk carrier ZYLEF on the gear housing fixed housing cover GD results in a structurally comparatively simple pressure and lubricant supply to both clutches E, F via corresponding channels or holes which extend in sections within said housing cover GD and partially within the hub of the disk carrier ZYLEF , A pressure medium supply to the pressure chamber 511 the servo device 510 the clutch E is with 516 denotes a lubricant supply to the pressure compensation chamber 512 the servo device 510 the clutch E with 517 , a pressure medium supply to the pressure chamber 611 the servo device 610 the clutch F with 616 , and a lubricant supply to the pressure compensation chamber 612 the servo device 610 the clutch F with 617 ,

Except for details of the pressure and lubricant supply to the two clutches E, F corresponds to in 6 shown component-side configuration of the assembly formed by the two clutches E, F with the common for both clutches E, F disc carrier ZYLEF, the servo devices 510 . 610 and the disk packs 500 . 600 the two clutches E, F thus corresponds in essential of in 2 shown component-side configuration of this module with the two clutches E, F.

The starting element 530 the clutch E is formed as an inner disk carrier, which is based on the disk set 500 the clutch E axially adjacent to the servo device 510 the clutch E extends radially inwardly to just above the drive shaft AN and in its hub region with the web shaft 540 is rotationally connected. This bridge wave 540 extends axially in the direction of the transfer gearset VS up to an area between the third sun gear S3_HS and the (spatially middle) first sun gear S1_HS of the main gearset HS, and passes centrally through the third sun gear S3_HS of the main gearset HS in the axial direction. In the mentioned range axially between the sun gears S3_HS and S1_HS is the ridge wave 540 ST13_HS of the main gearset HS connected rotationally fixed to the web plate of the transfer gearset coupled remote ST13_HS, said web plate of the web ST13_HS also rotationally fixed to the output element 430 the Haupradsetnah arranged brake D is connected.

The starting element 630 the clutch F is designed as an outer disk carrier, which is based on the disk set 600 the clutch F axially adjacent to the output member (or the inner disc carrier) 530 the clutch E to just above the web shaft 540 extends radially inward and rotationally fixed in its hub region with the (sun gear remote) third sun gear S3_HS of the main gearset HS. The just if kinematically coupled to the third sun gear S3_HS of the main gearset HS output element 330 The brake C is exemplary here in the range of the outer diameter of the outer disk carrier ( 630 ) of the clutch F with this outer disc carrier ( 630 ), in which the brake C is arranged, for example, directly axially next to the brake D on the side remote from the main wheel set.

Otherwise corresponds to in 6 shown component assembly substantially already in 4 illustrated arrangement.

Of course, the basis 6 described component assembly can also be combined with another main gearset type. A corresponding example of this will now be based on a in 7 illustrated sixth transmission systems according to the invention explained. The main gearset HS here is a three-way four-shaft planetary gear, which is reduced to a two -step planetary gear, now comprising three sun gears S1_HS, S2_HS and S3_S, three ring gears H1_HS, H2_HS and H3_S, a coupled web ST13_HS with rotatably mounted planet gears P1_HS and P3_HS, and a simple bridge ST2_HS with planetary gears P2_HS rotatably mounted thereon. In this case, the sun gear S1_HS, the ring gear H1_HS and the planet gears P1_HS meshing with this sun gear S1_HS and this ring gear H1_HS are assigned to the first of the three individual planetary gear sets of the main gearset HS. The sun gear S2_HS, the ring gear H2_HS and the planet gears P2_HS meshing with this sun gear S2_HS and this ring gear H2_HS are assigned to the second of the three individual planetary gear sets of the main gearset HS. Finally, the sun gear S3_HS, the ring gear H3_HS and the planetary gears P3_HS meshing with this sun gear S3_HS and this ring gear H3_HS are assigned to the second of the three individual planetary gear sets of the main gearset HS. Spatially speaking, said first of the three individual planetary gear sets of the main gearset HS is again arranged axially between the second planetary gear set of the main gearset HS close to the transfer gearset and the third third of the three individual planetary gear sets of the main gearset HS remote from the transfer gearset. The two sun gears S2_HS and S1_HS are firmly connected. As a further kinematic coupling of the main gearset HS, a fixed connection between the (simple) web ST2_HS and the two ring gears H1_HS and H3_HS is provided.

In a modification of the in 7 For example, it can also be provided that the two planetary gears P1_HS and P3_HS of the main gearset HS rotatably mounted on the coupled web ST13_HS are combined to form a stepped planet, whereby one of the two according to FIG 7 With the output shaft AB connected ring gears H1_HS, H3_HS of the main gearset HS can be omitted.

Based 8th Now, a seventh exemplary transmission scheme according to the present invention will be explained below, based on the previously described in FIG 6 described fifth gearbox according to the invention, the changes to this essentially relates only to the structural design of the assembly formed by the two clutches E and F. Unchanged, this module is arranged on the side of the main gearset HS facing away from the transfer gearset VS and comprises a disk carrier ZYLEF common to both clutches E and F, the servos 510 . 610 Both clutches E and F, and the disk packs 500 . 600 Both clutches E and F. This plate carrier ZYLEF forms for both clutches E and F their input element and is connected in rotation with the drive shaft AN.

As in 8th can be seen, is the disk set 600 the clutch F now spatially seen radially below the disk set 500 the clutch E arranged. Correspondingly, the disk carrier ZYLEF for the clutch F is an outer disk carrier for receiving externally toothed disks of the (now radially inner) disk set 600 formed of this clutch F, and for the clutch E as an inner disk carrier for receiving internally toothed disks of the (now radially outer) disk set 500 the clutch E. Accordingly, the spatial position of the servo devices 510 . 610 the two clutches E, F opposite 6 swapped and the servo device 610 the clutch F now closer to the main gearset HS arranged as the servo device 510 the clutch E. Insofar, the previously based 6 described in detail embodiment of these servos 510 . 610 analogously easily transferable, which is why their detailed detailed verbal description can be omitted here. In order to avoid misunderstandings, only the deviating and new reference numbers are mentioned here by name. So is 8th the - now assigned to the clutch F - hubshaft close hub section of the plate carrier ZYLEF with 623 denoted, the - now the clutch E attributable - far away from the wheel hub section of the plate carrier ZYLEF with 523 , To form the pressure chamber 511 the servo device 510 the clutch E is a support disk 518 provided, which at the main gearset remote hub section 523 fastened fluid-tight and against a partially meander-shaped piston 514 this servo device 510 pressure medium tight axially displaceable. In contrast to 6 are now the pressure chamber 611 the servo device 610 the clutch F and the pressure compensation chamber 512 the servo device 510 the clutch E arranged immediately adjacent to each other and separated only by a lateral surface of the disk carrier ZYLEF.

As in 8th further apparent, is the output element 630 the clutch F as opposed to 6 now designed as an inner disk carrier, which is based on the radially inner disk set 600 the assembly consisting of the clutches E and F axially adjacent to the servo device 610 the clutch F extends radially inwardly to just above the drive shaft AN and in its hub region with a third sun shaft 640 is rotationally connected. This third sun wave 640 surrounds the drive shaft AN radially and extends axially in the direction of the transfer gearset VS and passes through the main gearset HS centric in the axial direction completely. Rotationally connected is this third sun wave 640 on the one hand also with the (spatially middle) first sun gear S1_HS and the second sun gear S2_HS of the main gearset HS (close to the transfer gearset), and on the other hand (spatially in a range axially between the transfer gearset VS and the main gearset HS) with the output element 230 the clutch B. The output element 330 the brake C is directly connected rotationally fixedly to the third sun gear S3_HS of the main gearset HS (in the example remote from the transfer gearset), in the illustrated example in sections axially directly adjacent to the main gearset HS.

In contrast to 6 is in 8th the starting element 530 the clutch E now designed as an outer disk carrier. Starting from the radially outer disc pack 500 consisting of the clutches E and F assembly extends this outer plate carrier ( 530 ) of the clutch E sections at least substantially parallel axially between the output element (inner disk carrier) 630 the clutch F and the output element 330 the brake C radially inward to a diameter just above the third sun shaft 640 , In its hub area is the inner disk carrier ( 530 ) of the clutch E in turn with the web shaft 540 rotationally connected, which is the third sun wave 640 encloses radially. As in 6 passes through the bridge shaft 540 the third sun gear S3_HS of the main gearset HS in the axial direction between the sun gears S3_HS and S1_HS is connected in a rotationally fixed manner to the web plate of the coupled web ST13_HS of the main gearset HS in the region axially between the sun gears S3_HS and S1_HS.

Otherwise corresponds to in 8th shown component assembly already in 6 illustrated arrangement.

Of course, also the basis 8th described component assembly can also be combined with another main gearset type. A corresponding example is in 9 shown as an eighth gearbox according to the invention. The main gearset HS is here a three-way four-shaft planetary gear, which is reduced to a two -step planetary gear and identical to that in 7 illustrated main gearset HS is constructed, which is why at this point can be dispensed with its detailed description again.

Based 10 Now, a ninth exemplary transmission scheme according to the present invention will be explained, again based on the 8th described seventh transmission scheme according to the invention, but with a too 8th second alternative main gearset HS and with one to 8th alternative structural design of the assembly with the fifth and sixth switching element E, F.

As in 10 can be seen, is the "new" Main gearset HS is now formed as a two-staged four-shaft planetary gear with three input elements and an output element comprising two coupled single planetary gear sets, of which the first is in a single planetary construction and the second in a double planetary design. The second simple planetary gearset of the main gearset HS is the Vorschaltradsatz VS applied and includes a sun gear S2_HS, a ring gear H2_S, and a coupled web ST2_HS with rotatably mounted thereon inner and outer planetary gears PLi_HS, PLa_HS. The inner planet gears PLi_HS mesh with the sun gear S2_HS and the outer planet gears PLa_HS, the outer planet gears PLa_HS with the inner planet gears PLi_HS and the ring gear H2_HS. The first simple planetary gear set of the main gearset HS is arranged on the side of the second simple planetary gear set of the main gearset HS facing away from the transfer gearset VS and comprises a sun gear S1_HS, a ring gear H1_S, and a web ST1_HS with planet gears PL_HS rotatably mounted thereon. The planet gears PL_HS mesh with the sun gear S1_HS and the ring gear H1_HS.

The first sun gear S1_HS and the coupled second web ST2_HS of the main gearset HS are connected to each other rotationally fixed and form the first input element of the main gearset HS, which is connected to the output elements 230 . 630 the two clutches B, F and the output element 330 the brake C is connected. Here are the output elements 230 . 630 the clutches B, F on the first sun shaft 240 rotatably connected to the sun gear S1_HS, the output element 330 the brake C, however, is rotationally connected to a starter plate side web plate of the web ST2_HS. The input element 220 the clutch B in turn is connected to the ring gear HO_VS of the transfer gearset VS. The input element 620 the clutch F in turn is connected to the drive shaft AN. The input element 320 the brake C in turn is connected to the transmission housing GG or integrated in the transmission housing GG.

The gearset near the second sun gear S2_HS of the main gearset HS forms the second input element of the main gearset HS and is connected to the output element 130 the clutch A connected. The input element 120 the clutch A in turn is connected to the ring gear HO_VS of the transfer gearset VS.

The first web ST1_HS and the second ring H2_HS of the main gearset HS are connected to each other and form the third input element of the main gearset HS, which in turn with the output element 530 the clutch E and the output element 430 the brake D is connected. Here is the starting element 530 the clutch E rotatably connected to a Stegradsatz remote web plate of the web ST1_HS, the output element 430 the brake D, however, is rotationally connected to the ring gear H2_HS or to a web plate of the web ST1_HS close to the transfer gearset. The input element 520 the clutch E in turn is connected to the drive shaft AN. The input element 420 the brake D in turn is connected to the transmission housing GG or integrated in the transmission housing GG.

The transfer ring remote first ring gear H1_HS of the main gearset HS forms the output element of the main gearset HS and is connected to the output shaft AB of the transmission. In the in 10 illustrated embodiment, the output shaft AB coaxial with the drive shaft AN. The skilled person will but if necessary, the output shaft AB deviating from the illustration in 10 also arrange parallel to the axis or at an angle to the drive shaft AN.

The switching logic of this ninth transmission scheme according to the invention 10 corresponds to the in 1B shown switching logic of the generic transmission.

The spatial arrangement of the six switching elements A to F within the gear housing GG is based on their previously described respective kinematic connection to the individual components of the main gearset HS. As in 10 can be seen, the brake C with its disc pack 300 and their servo 310 arranged in the region of the inner diameter of the gear housing GG, spatially seen predominantly axially next to the main gearset HS on its vorschaltradsatznahen side, but partially also radially above the second ring gear H2_HS close to the main gearset HS. If necessary, the skilled person, the brake C deviating from the illustration in 10 for example, in a region near the gear housing fixed housing wall GW on the main gearset remote side of the transfer gearset VS arrange. As in 10 Furthermore, it can be seen that the brake D with its disc pack 400 and their servo 410 also arranged in the region of the inner diameter of the gear housing GG, but spatially seen in a region radially above the main gearset HS and thereby approximately radially over the second ring gear H2_HS of the main gearset HS close to the transfer gearset.

As in 10 Furthermore, it can be seen, the clutch A connects axially directly to the main gearset HS on its side near the transfer gearset side. In this case, the output connected to the second sun gear S2_HS of the main gearset HS is off transition element 130 the clutch A formed as a cylindrical outer disk carrier, geometrically in the form of a direction of the transfer gear VS open pot, within which the disk set 100 the clutch A and the servo device 110 the clutch A for actuating this plate pack 100 are arranged. Accordingly, the servo device rotates 110 the clutch A always with speed of the second sun gear S2_HS of the main gearset HS. The corresponding formed as an inner disk carrier input element 120 the clutch A is above the input element 220 the clutch B with the ring gear HO_VS the Vorschaltrad set VS rotationally connected. The clutch B in turn is partially disposed on the main gearset remote side of the transfer gearset VS and partially radially over the transfer gearset VS, wherein the disk set 200 the clutch B at least partially radially above the ring gear HO_VS of the transfer gearset VS and the servo device 210 the clutch B to operate this disc pack 200 at least predominantly on the opposite side of the main gearset HS of the transfer gearset VS is arranged. The input element connected to the ring gear HO_VS 220 the clutch B is formed as a cylindrical outer disk carrier, geometrically in the form of a direction of the main gearset HS towards open pot, within which the disk set 200 and the servo 210 the clutch B are arranged. The correspondingly designed as an inner disk carrier output element 230 The clutch B is directly adjacent to this transfer gearset VS on the side of the transfer gearset VS facing the main gearset HS and is in its hub region for kinematic connection to the first sun gear S1_HS (and the transfer gearset distant web plate of the second land ST2_HS) of the main gearset HS with the already mentioned first sun wave 240 rotationally connected. The first sun wave 240 in turn surrounds the drive shaft AN and passes through in its axial course, starting from the hub of the output element 230 or inner disk carrier of the clutch B first through the output element 130 or the outer disk carrier of the clutch A formed clutch space of the clutch A centric complete and then also the vorschaltradsatznahe second sun S2_HS of the main gearset HS centric complete.

As in 10 Furthermore, it can be seen that the two clutches E and F form a preassemblable in manufacturing technology preassembled module, comprising a common for both clutches E, F disc carrier ZYLEF, for both clutches E, F depending a disk set 500 respectively. 600 as well as for both clutches E, F one servo device each 510 respectively. 610 for actuating the respective disk pack 500 respectively. 600 , Similar to in 8th this assembly is arranged on the opposite side of the transfer gearset VS side of the main gearset HS, spatially seen between a gear housing fixed housing cover GD, which forms the housing wall GW opposite outer wall of the transmission, and the main gearset HS and axially adjacent to this main gearset HS.

The common for the two clutches E, F disc carrier ZYLEF forms for both clutches E, F whose input element and is correspondingly rotationally connected to the drive shaft AN, which for this purpose almost fully engages through the entire transmission in the axial direction. The slat package 500 the clutch E is spatially at least substantially radially over the disk pack 600 arranged the clutch F, wherein both disc packs 500 . 600 adjacent to the main gearset HS - in particular adjacent to the first ring gear H1_HS - are arranged. Correspondingly, the disk carrier ZYLEF for the clutch F is an outer disk carrier for receiving externally toothed disks of the radially inner disk pack 600 formed this assembly, and for the clutch E as an inner disk carrier for receiving internally toothed fins of the radially outer disk set 500 this assembly. Also on the main wheel set remote side of the disk pack 500 arranged servo device 510 The clutch E is spatially at least substantially radially above the far away on the main gearset side of the disk set 600 arranged servo device 610 arranged the clutch F.

Geometrically, the plate carrier ZYLEF is designed as a pot open towards the main gearset HS, with a stepped cylindrical section 621 respectively. 521 , a pot bottom 622 and with a hub 623 , In the area of its hub near the end of the stepped cylindrical section of the plate carrier ZYLEF at its inner diameter has a Mitnah meprofil for receiving the outer plates of the plate pack 600 the clutch F and at its outer diameter a driving profile for receiving the inner disks of the disk set 500 the clutch E on. Accordingly, the outer diameter of the stepped cylindrical portion of the plate carrier ZYLEF with 521 designated and the inner diameter of this stepped cylindrical section with 621 , At the main gear set remote end of the stepped cylindrical section 621 respectively. 521 of the plate carrier ZYLEF closes the disc-shaped pot bottom 622 and extends radially inwardly to a diameter just above the output shaft AB of the transmission. At the inside diameter of this pot bottom 622 in turn the hub closes 623 of the plate carrier ZYLEF and extends axially in the direction of the main gearset HS. Here is this hub 623 rotatably mounted on the output shaft AB. The Output shaft AB in turn is rotatably mounted in the housing cover GD and penetrates this housing cover GD centrally in the axial direction. Should differ in another embodiment of the transmission scheme to the representation in 10 the output shaft AB should not be arranged coaxially with the drive shaft AN, so the hub would be 623 of the disk carrier ZYLEF then suitably rotatably mounted on an axially in the direction of the main gearset HS in the transmission interior extending gear housing fixed pin of the housing cover GD.

As in 10 further apparent is the servo device 610 the clutch F spatially seen radially above the hub 623 of the plate carrier ZYLEF completely arranged within a cylinder space, which is defined by the plate carrier ZYLEF, more precisely by the stepped cylindrical section 621 and the bottom of the pot 622 of the plate carrier ZYLEF is formed. Because the servo device 610 At this plate carrier ZYLEF is mounted axially displaceable, it rotates constantly with speed of the drive shaft AN. In this case, the servo device includes 610 a pressure room 611 , a pressure equalization room 612 , a piston 614 , a reset element 613 and a baffle plate 615 , The piston 614 is mounted axially displaceable in the plate carrier ZYLEF fluid-tight and over the example here designed as a plate spring return element 613 axially against the hub 623 of the plate carrier ZYLEF biased. The pressure room 611 is formed by the piston 614 and a part of the inner circumferential surface of the plate carrier ZYLEF. To compensate for the rotary pressure of the rotating pressure chamber 611 is a dynamic pressure equalization with the pressure equalization chamber 612 provided, this pressure equalization space 612 through the piston 614 and the baffle plate 615 is formed and arranged closer to the main gearset HS than the pressure chamber 611 ,

The pressure medium and lubricant supply of the servo device 610 The coupling F is carried out via corresponding channels or bores, which are partially within the housing wall GW and partially within the output shaft AB and partially within the hub 623 of the plate carrier ZYLEF. A pressure medium supply to the pressure chamber 611 the servo device 610 the clutch F is with 616 denotes a lubricant supply to the pressure compensation chamber 612 the servo device 610 the clutch F with 617 , Will the pressure chamber 611 for closing the clutch F acted upon by pressure medium, the piston moves 614 axially in the direction of the main gearset HS and actuates the disk set associated with it 600 against the spring force of the return element 613 ,

The servo device 510 The radially outer clutch E is spatially in a region radially above the servo device 610 the radially inner clutch F is arranged. This servo device 510 includes a pressure chamber 511 , a pressure compensation room 512 , a piston 514 , a reset element 513 and a support disk 518 , Here is the pressure chamber 511 the servo device 510 the (radially outer) clutch E at least approximately radially above the pressure chamber 611 the servo device 610 the (radially inner) clutch F and the pressure compensation chamber 512 the servo device 510 the (radially outer) clutch E at least approximately radially above the pressure equalization space 612 the servo device 610 the (radially inner) clutch F is arranged. The named pressure chamber is formed 511 through the piston 514 , the support disk 518 and a part of the outer surface of the plate carrier ZYLEF. For this purpose, the support disk 518 geometrically in the form of a lamella packet 500 or in the direction of the main gearset HS open pot formed, the lateral surface of the piston 514 surrounds outside, and the bottom of the pot is attached at its inner diameter on the outer diameter of the disc-shaped portion of the plate carrier ZYLEF. In the example shown is for the attachment of the support disk 518 on the plate carrier ZYLEF a pressure-sealed sealing driving profile and for axial fixing a locking ring provided. Thus, the piston 514 between the inner diameter of the cylindrical portion of the support disk 518 and the outer diameter of the stepped cylindrical portion of the plate carrier ZYLEF pressure-tight axially displaceable and mounted on the return element 513 axially biased against the plate carrier ZYLEF. The reset element 513 is here exemplified as a spring assembly of annularly arranged coil springs.

A pressure medium supply 516 to the pressure room 511 the servo device 510 the clutch E runs in sections within the housing wall GW and sections within the output shaft AB and partially within the pot bottom 622 of the plate carrier ZYLEF. The pressure compensation room 512 the servo device 510 the (radially outer) clutch E is here in a construction-saving manner directly on the pressure compensation chamber 612 the servo device 610 the (radially inner) clutch F pressureless filled with lubricant. This is the outer diameter of the piston 614 the servo device 610 provided at least one radial bore on the one hand in the pressure compensation chamber 612 the servo device 610 and on the other hand in an outwardly sealed lubricant seal annulus on the inner diameter of the stepped cylindrical portion 621 of the plate carrier ZYLEF opens. Furthermore, in the stepped cylindrical section 621 of the disk carrier ZYLBF provided at least one radial bore, on the one hand in said annular space on the inner diameter of the stepped cylindrical portion 621 and on the other hand in the pressure equalization room 512 the servo device 510 empties. The corresponding holes or channels between the two pressure equalization chambers 612 . 512 are in 10 With 517 designated. Will the pressure chamber 511 the servo device 510 to close the clutch E filled with pressure medium, so the piston moves 514 axially in the direction of the main gearset HS and actuates the disk set associated with it 500 against the spring force of the return element 513 ,

Of course, in another embodiment of the two clutches E and F comprehensive assembly may be provided that different from the representation in 10 the servos 510 . 610 the two clutches E, F are arranged largely side by side, as for example in 8th is proposed.

As in 10 further apparent, is the output element 630 the clutch F is formed as a largely disc-shaped inner disk carrier which is rotationally fixed in its hub region with the first sun gear S1 HS of the main gearset HS remote from the transfer gearset. The starting element 530 the clutch E is designed as a cylindrical outer disk carrier, which is rotationally connected to the transfer gearset distant web plate of the first web ST1_HS of the main gearset HS and here by way of example to the first sun shaft 240 or a hub of the output element 630 or inner disk carrier of the clutch F is rotatably mounted. In this case, the aforementioned transfer gearset distant web plate of the web ST1_HS and the output element 530 or the outer disk carrier of the clutch E also be made in one piece.

For speed and torque transmission between the transfer gearset distant first ring gear H1_HS of the main gearset HS and here exemplarily coaxial to the drive shaft AN extending output shaft AB, a connecting element ZYLH is provided, which geometrically in the form of a direction towards the main gear HS open pot with a disc-shaped pot bottom and a cylindrical ring Sheath is formed and completely encloses the assembly formed from the two clutches E, F. In this case, the pot bottom of this connecting element ZYLH is rotationally connected to the output shaft AB (here welded by way of example) and extends in the radial direction axially between the pot bottom 622 of the plate carrier ZYLEF and the housing wall GW. At its end near the main gearset end, the cylinder-shaped shell of the connecting element ZYLH is connected to the ring gear H1_HS in a rotationally fixed manner (for example with a positive fit).

Based 11 Now, a tenth exemplary transmission scheme according to the present invention will be explained based on the above 10 described ninth gearbox according to the invention, but with a too 10 In this respect, the explanation of this tenth transmission scheme according to the invention can be limited to the description of this modified assembly.

As in 11 can be seen, the said assembly still comprises a common plate carrier ZYLEF, which forms the input element for both clutches E, F and is correspondingly connected to the drive input shaft AN of the transmission, for both clutches E, F respectively a disc pack 500 respectively. 600 and for both clutches E, F each have a Servoeinrich device 510 respectively. 610 for actuating the respective disk pack 500 respectively. 600 , In contrast to 10 are the disk packs 500 . 600 the two clutches E, F now axially juxtaposed, preferably on the same or on an at least similar diameter.

In the in 11 illustrated embodiment, the common for both clutches E, F, with the drive shaft AN rotationally connected plate carrier ZYLEF is now formed for both clutches E, F as outer disc carrier. According to the kinematic connection of the (now designed as an inner disc carrier) output element 530 the clutch E to the (connected to the second ring gear H2_HS) first web ST1_HS of the main gearset HS and corresponding to the kinematic connection of the (designed as an inner disk carrier) output element 630 the clutch F to the first sun gear S1_HS of the main gearset HS is the disk set 500 the clutch E arranged closer to the main gearset HS than the disk set 600 the clutch F.

Geometrically, the plate carrier ZYLEF is designed as a pot open towards the main gearset HS, with a stepped cylindrical section 621 respectively. 521 , a pot bottom 622 and with a hub 623 , In the area of its hub near the end of the gearset, the stepped cylindrical section of the disk carrier ZYLEF has a driving profile on its inner diameter for receiving the outer disks of the disk pack 500 the clutch E on. Accordingly, this part of the stepped cylindrical portion of the plate carrier ZYLEF with 521 designated. In the area approximately in the middle of its axial extent, the stepped cylindrical section of the plate carrier ZYLEF has at its in nendurchmesser a driving profile for receiving the outer disk of the disk pack 600 the clutch F on. Accordingly, this part of the stepped cylindrical portion of the plate carrier ZYLEF with 621 designated. At the main gear set distal end of the stepped cylindrical section ( 621 ) of the disk carrier ZYLEF closes the disk-shaped pot bottom 622 and extends radially inwardly to a diameter just above the output shaft AB of the transmission. At the inside diameter of this pot bottom 622 in turn the hub closes 623 of the plate carrier ZYLEF and extends axially in the direction of the main gearset HS. Here is this hub 623 rotatably mounted on the output shaft AB. The output shaft AB in turn is rotatably mounted in the housing cover GD and penetrates this housing cover GD centrally in the axial direction. Should differ in another embodiment of the gearbox schemes to the representation in 11 the output shaft AB should not be arranged coaxially with the drive shaft AN, so the hub would be 623 of the disk carrier ZYLEF then suitably rotatably mounted on an axially in the direction of the main gearset HS in the transmission interior extending gear housing fixed pin of the housing cover GD.

As in 11 further apparent is the servo device 610 the clutch F is spatially radially above the hub 623 of the plate carrier ZYLEF completely disposed within a cylinder space, which is through the stepped cylindrical section 621 and the bottom of the pot 622 of the plate carrier ZYLEF is formed. As in 10 includes the servo device 610 a pressure room 611 , a pressure compensation room 612 , a piston 614 , a reset element 613 and a baffle plate 615 , The piston 614 is mounted axially displaceable in the plate carrier ZYLEF fluid-tight and over the example here designed as a plate spring return element 613 axially against the hub 623 of the plate carrier ZYLEF biased. The pressure room 611 is formed by the piston 614 and a part of the inner circumferential surface of the plate carrier ZYLEF. To compensate for the rotational pressure of the constantly rotating at rotational speed of the drive shaft AN pressure chamber 611 is a dynamic pressure equalization with the pressureless with lubricant fillable pressure compensation chamber 612 provided, this pressure equalization space 612 through the piston 614 and the baffle plate 615 is formed and arranged closer to the main gearset HS than the pressure chamber 611 , The pressure medium and lubricant supply 616 respectively. 617 to the servo device 610 the clutch F is off 10 unchanged. Will the pressure chamber 611 for closing the clutch F acted upon by pressure medium, the piston moves 614 axially in the direction of the main gearset HS and actuates the disk set associated with it 600 against the spring force of the return element 613 , Relative to the spatial position of their pressure chamber 611 operates the servo 610 the plate set associated with it 600 when closing the clutch F thus "pressed".

In contrast to 10 operates the servo 510 the clutch E the assigned her plate set 500 when clutch closing in the tenth invention according to the transmission 11 In contrast, "pulled." In the in 11 illustrated embodiment, this servo device 510 the clutch E substantially radially above the servo device 610 arranged the clutch F. A pressure room 511 the servo device 510 The clutch E is spatially now now in something radially above the pressure compensation chamber 612 the servo device 610 arranged the clutch F. Accordingly, to compensate for the dynamic pressure of always rotating at rotational speed of the drive shaft AN pressure chamber 511 provided pressure equalization space 512 the servo device 510 the clutch E spatially seen now approximately radially above the pressure chamber 611 the servo device 610 arranged the clutch F. The named pressure chamber is formed 511 the servo device 510 through a piston 514 this servo device 510 and by a radially outside of the clutch space of the clutch F lying lateral surface of the disk carrier ZYLEF, so that the axially displaceably mounted on the disk carrier ZYLEF piston 514 is arranged substantially radially above the stepped cylindrical portion of this disk carrier ZYLEF. In the illustrated embodiment, this is the disk pack 500 the clutch E associated pressure chamber 511 spatially seen axially next to the disk pack 600 arranged the clutch F. For actuation of the associated plate pack 500 points the piston 514 the servo device 510 the clutch E one of the hauptradsatznahen side of this disk set 500 out on the disk pack 500 acting pressure plate. Instead of this pressure plate, for example, a plurality of circumferentially distributed actuating fingers may be provided. The piston 514 or the pressure plate or the actuating fingers of this piston 514 embrace the two side-by-side lamella packages 500 and 600 radially completely in the axial direction. The on the the lamella package 500 opposite side of the pressure chamber 511 arranged, pressure-free filled with lubricant pressure compensation chamber 512 the servo device 510 the clutch E is formed by the piston 514 and through a cup-shaped baffle plate 515 , This baffle plate 515 is outside of the plate carrier ZYLEF in the area of the bottom of the pot 622 fixed and opposite the piston 514 axially displaceable sealed lubricant seal. A pressure medium and lubricant supply 516 respectively. 517 to the servo device 510 the clutch E is similar to that in 10 , At a filling of the pressure chamber 511 with pressure medium, the piston moves 514 axially in opposite direction to the main gearset HS direction against the spring force of the return element 513 which is exemplified here as an axial between pistons 514 and baffle plate 515 clamped coil spring package is formed.

Otherwise corresponds to in 11 shown component assembly of the basis 10 already explained in detail arrangement.

Of course, in another embodiment of the two clutches E and F comprehensive assembly may also be provided that different from the representation in 11 the servos 510 . 610 the two clutches E, F are at least largely juxtaposed, as for example in 8th is proposed, in which case similar to in 10 one on the disk pack 500 the clutch E acting pressure plate or preferably a plurality of circumferentially distributed arranged on the disk set 500 the actuator E acting actuator of the piston 514 the servo device 510 the two side-by-side disk packs 600 . 500 must encompass radially outward in the axial direction.

In yet another embodiment of the assembly comprising the two clutches E and F, it may also be provided, for example, that the plate packs 500 . 600 the two clutches E, F as in 11 Although arranged directly next to each other, the disk set 600 the clutch F but different from the representation closer to the main gearset HS is arranged as the disk set 500 the clutch E. According to the kinematic connection of the output element 530 the clutch E to the (connected to the second ring gear H2_HS) first web ST1_HS the main gearset HS and according to the kinematic connection of the output element 630 In this case, the clutch F to the first sun gear S1_HS of the main gearset HS must be designed as the disk carrier ZYLEF common to both clutches E, F for both clutches E, F as the inner disk carrier and the output element then designed as an outer disk carrier 530 the clutch E then also designed as an outer disc carrier output element 630 engage around the clutch F in the axial direction radially outward. In general, the practical construction of this embodiment variant will lead to the servo device 610 the clutch F is arranged substantially closer to the main gearset HS as the servo device 510 the clutch E. In particular, a pressure chamber 611 the servo device 610 As a rule, the clutch F will then be arranged closer to the main gearset HS than a pressure chamber 511 the servo device 510 the clutch E. Depending on the available space, the servo device 510 the clutch E spatially seen at least substantially radially over the Servooeinrichtung 610 the clutch F or at least largely on the main gearset HS opposite side of the servo device 610 be arranged the clutch F. Deviating from 11 operates the servo 610 the plate set associated with it 600 when closing the clutch F in this embodiment variant axially in opposite direction to the main gearset HS direction, based on the spatial position of their pressure chamber 611 So "pulled", whereas the servo device 510 the plate set associated with it 500 when closing the clutch E is actuated axially in the direction of the main gearset HS, based on the spatial position of their pressure chamber 511 Thus, if a dynamic pressure equalization is provided for the clutch F, the pressure chamber would be 611 the servo device 610 the clutch F then closer to the main gearset HS arranged as a required for said dynamic pressure compensation pressure compensation chamber 612 this servo device 610 , If a dynamic pressure equalization is provided for the clutch E, a pressure equalization chamber required for this dynamic pressure compensation would be required 512 the servo device 510 the clutch E then expediently closer to the main gearset HS arranged as the pressure chamber 511 the servo device 510 regardless of the already mentioned possible spatial position of this servo device 510 radially above or axially adjacent the servo 610 A sketch of a possible construction of this proposed embodiment variant of the assembly formed by the clutches E, F is in 12 shown.

Shooting was Once again noted that in the various component assemblies according to the invention synonymous with the different previously explained Main gear set variants can be combined.

A

first Switching element, coupling

B

second Switching element, coupling

C

third Switching element, brake

D

fourth Shaft element, brake

e

fifth switching element, clutch

F

sixth Switching element, coupling

AT

drive shaft

FROM

drive shaft

DG

housing cover

GG

gearbox

GN

hub the housing wall

GW

housing wall

GZ

Housing partition

NAN

tooth profile for driving speed determination

ZYL

cylindrical connecting element

ZYLB

cylindrical connecting element

ZYLF

cylindrical connecting element

ZYLH

connecting element

ZYLAB

common plate carrier of the first and second switching

element

ZYLBF

common plate carrier of the second and sixth switching

element

ZYLCD

common plate carrier the third and fourth shift

element

ZYLEF

common plate carrier of the fifth and sixth switching

element

VS

gearset

HO_VS

ring gear of the transfer gearset

SO_VS

sun of the transfer gearset

ST_VS

(Coupled) Bridge of the transfer gearset

P1_VS

inner Planetary gear of the transfer gearset

P2_VS

outer planetary gear of the transfer gearset

HS

main gear

H1_HS

first Ring gear of the main gearset

H2_HS

second Ring gear of the main gearset

H23_HS

coupled (second) ring gear of the main gearset

S1_HS

first Sun gear of the main gearset

S2_HS

second Sun gear of the main gearset

S3_HS

third Sun gear of the main gearset

ST1_HS

first Footbridge of the main wheel set

ST2_HS

second Footbridge of the main wheel set

ST13_HS

coupled (second) bridge of the main gearset

P13_HS

long Planetary wheel of the main gearset

P2_HS

short Planetary wheel of the main gearset

PL_HS

first Planetary wheel of the main gearset

PLa_HS

outer planetary gear of the main gearset

PLi_HS

inner Planetary wheel of the main gearset

100

slats of the first switching element

110

servo of the first switching element

111

pressure chamber the servo of the first switching element

112

Pressure equalization chamber the servo of the first switching

element

113

Return element the servo of the first switching element

114

piston the servo of the first switching element

115

baffle plate the servo of the first switching element

120

input element of the first switching element

123

hub the input element of the first (and second) switching element

mentes

130

output element of the first switching element

140

second sun wave

150

driving plate

200

slats of the second switching element

210

servo of the second switching element

211

pressure chamber the servo of the second switching element

212

Pressure equalization chamber the servo of the second switching

element

213

Return element the servo of the second switching element

214

piston the servo of the second switching element

215

baffle plate the servo of the second switching element

216

Pressure medium supply to Pressure chamber of the servo device of

second switching element

217

Lubricant supply to Pressure equalization chamber of the servo unit

tung of the second switching element

218

support disc the servo of the second switching element

219

hub the servo of the second switching element

220

input element of the second switching element

223

hub the input element of the second switching element

230

output element of the second switching element

233

hub the output element of the second switching element

240

first sun wave

250

Take sheet

300

slats of the third switching element

310

servo of the third switching element

311

pressure chamber the servo of the third switching element

313

Return element the servo of the third switching element

314

piston the servo of the third switching element

320

input element of the third switching element

330

output element of the third switching element

400

slats of the fourth switching element

410

servo of the fourth switching element

411

Pressure chambers of Servo device of the fourth switching element

413

Return element the servo of the fourth switching element

414

piston the servo of the fourth switching element

420

input element of the fourth switching element

430

output element of the fourth switching element

500

slats of the fifth shaft element

510

servo of the fifth switching element

511

pressure chamber the servo of the fifth switching element

512

Pressure equalization chamber the servo of the fifth switching

element

513

Return element the servo of the fifth switching element

514

piston the servo of the fifth switching element

515

baffle plate the servo of the fifth switching element

520

input element of the fifth switching element

521

cylindrical Section of the input element of the fifth switching

element

522

disc-shaped section of the input element of the fifth

switching element

523

hub of the input element of the fifth switching element

530

output element of the fifth switching element

540

web shaft

600

slats of the sixth switching element

610

servo of the sixth switching element

611

pressure chamber the servo of the sixth switching element

612

Pressure equalization chamber the servo of the sixth shift

element

613

Return element the servo of the sixth shift

element

614

piston the servo of the sixth switching element

615

baffle plate the servo of the sixth switching element

616

Pressure medium supply to Pressure chamber of the servo device of

sixth switching element

617

Lubricant supply to Pressure equalization chamber of the servo unit

tung of the sixth switching element

618

support disc the servo of the sixth switching element

620

input element of the sixth switching element

621

cylindrical Section of the input element of the sixth

switching element

622

disc-shaped section of the input element of the sixth

switching element

623

hub the input element of the sixth switching element

630

output element of the sixth switching element

633

hub the output element of the sixth switching element

640

third sun wave

Claims (50)

Multi-speed automatic transmissions, with a drive shaft (AN), an output shaft (AB), a transfer gearset (VS), a main gearset (HS) and at least six shift elements (A to F), with the following features: • the transfer gearset (VS) is considered • a planetary gearset (VS) output element rotates at a speed lower than the input shaft input speed (AN) • an input element of the transfer gearset (VS) is constantly connected to the input shaft (AN) • on Element of the transfer gearset (VS) is connected to a gearbox (GG) of the multi-stage automatic transmission, • the main gearset (HS) is designed as a coupled planetary gear set with several non-coupled input elements and an output element, • the output element of the main gearset (HS) is constantly connected to the output shaft (AB), • an input element ( 120 ) of the first switching element (A) is connected to the output element of the transfer gearset (VS), • an output element ( 130 ) of the first switching element (A) is connected to a second input element of the main gearset (HS), • an input element ( 220 ) of the second switching element (B) is connected to the output element of the transfer gearset (VS), • an output element ( 230 ) of the second shift element (B) is connected to a first input element of the main gearset (HS), • an input element of the third shift element (C) is connected to the transmission housing (GG), • an output element ( 330 ) of the third switching element (C) is adjacent to the first input element of the main gearset (HS) or one in a speed plan for this first input element an input element of the fourth switching element (D) is connected to the transmission housing (GG), • an output element ( 430 ) of the fourth switching element (D) is connected to a third input element of the main gearset (HS), • an input element ( 520 ) of the fifth switching element (E) is connected to the drive shaft (AN), • an output element ( 530 ) of the fifth shift element (E) is connected to the third input element of the main gearset (HS), • an input element ( 620 ) of the sixth switching element (F) is connected to the drive shaft (AN), • an output element ( 630 ) of the sixth shifting element (F) is connected to the first input element of the main gearset (HS) or to an input element of the main gearset (HS) adjacent to this first input element, characterized in that the fifth and sixth shifting elements (E, F) are a Form assembly, comprising a for the fifth and sixth switching element (E, F) common plate carrier (ZYLEF), each a plate pack ( 500 . 600 ) for the fifth and sixth switching element (E, F), and in each case a servo device ( 510 . 610 ) for the fifth and sixth switching element (E, F) for actuating the respective disk pack ( 500 . 600 ) of the fifth and sixth switching element (E, F). Multi-stage automatic transmission according to claim 1, characterized in that the fifth and sixth shift element (E, F) common disc carrier (ZYLEF) the input element ( 520 ) of the fifth switching element (E) and the input element ( 620 ) of the sixth switching element (F) forms. Multi-stage automatic transmission according to claim 1 or 2, characterized in that the assembly of the fifth and sixth switching element (E, F) spatially seen at least predominantly on the main gearset (HS) side facing away from the Vorschaltradsatzes (VS) is arranged 2 + 3 ]. Multi-stage automatic transmission according to claim 3, characterized in that the first and second switching elements (A, B) are arranged at least predominantly on the side of the transfer gearset (VS) which is opposite to the assembly of the fifth and sixth shift elements (E, F) [ 2 + 3 ]. Multi-stage automatic transmission according to claim 3 or 4, characterized in that the first switching element (A) is arranged closer to the transfer gearset (VS) than the second shift element (B) [ 2 + 3 ]. Multi-stage automatic transmission according to claim 3, 4 or 5, characterized in that the first switching element (A) axially directly adjacent to the transfer gearset (VS) on the main gearset (HS) facing side of the transfer gearset (VS) 2 + 3 ]. Multi-stage automatic transmission according to one of claims 3 to 6, characterized in that the output element ( 530 ) of the fifth switching element (E) or one with this output element ( 530 ) of the fifth switching element (E) connected connecting element (ZYL) the transfer gearset (VS) and the first and second switching element (A, B) in the axial direction radially completely overlaps, and that the output element ( 630 ) of the sixth switching element (F) the output element ( 530 ) of the fifth switching element (E) or with the output element ( 530 ) of the fifth switching element (E) connected connecting element (ZYL) in the axial direction radially at least largely overlaps [ 2 ]. Multi-stage automatic transmission according to one of claims 3 to 6, characterized in that the output element ( 630 ) of the sixth switching element (F) or one with this output element ( 630 ) of the sixth switching element (F) connected connecting element (ZYL) the transfer gearset (VS) and the first and second switching element (A, B) in the axial direction radially completely overlaps, and that the output element ( 530 ) of the fifth switching element (E) the output element ( 630 ) of the sixth switching element (F) or that with the output element ( 630 ) of the sixth switching element (F) connected connecting element (ZYL) in the axial direction radially at least largely overlaps ( 3 ]. Multi-stage automatic transmission according to one of claims 3 to 8, characterized in that the third and / or fourth switching element (C, D) on the side of the transfer gearset (VS) is arranged, the assembly of the fifth and sixth switching element (E, F) opposite [ 2 + 3 ]. Multi-stage automatic transmission according to claim 1 or 2, characterized in that the assembly of the fifth and sixth switching element (E, F) spatially seen at least predominantly in a range between the transfer gearset (VS) and main gearset (HS) is arranged axially [ 4 + 5 ]. Multi-stage automatic transmission according to claim 10, characterized in that the assembly of the fifth and sixth switching element (E, F) spatially seen at least partially radially under a disc pack ( 200 ) of the second switching element (B) is arranged, the initial element ( 230 ) of the second switching element (B), the assembly of the fifth and sixth switching element (E, F) in the axial direction radially at least partially overlaps [ 4 + 5 ]. Multi-stage automatic transmission according to claim 10 or 11, characterized in that the assembly of the fifth and sixth switching element (E, F) spatially seen at least partially radially under a disc pack ( 100 ) of the first switching element (A) is arranged [ 4 + 5 ]. Multi-stage automatic transmission according to claim 10, 11 or 12, characterized in that the third and / or fourth switching element (C, D) are arranged on the side of the main gearset (HS), which is opposite to the transfer gearset (VS) [ 4 + 5 ]. Multi-stage automatic transmission according to claim 1 or 2, characterized in that the assembly of the fifth and sixth switching element (E, F) spatially seen at least predominantly on the Vorschaltradsatz (VS) facing away from the main gearset (HS) is arranged 6 - 11 ]. Multi-stage automatic transmission according to claim 15, characterized in that the first and second shifting elements (A, B) are arranged at least predominantly on the side of the main gearset (VS) which is opposite the assembly of the fifth and sixth shifting elements (E, F) [ 6 - 11 ]. Multi-stage automatic transmission according to claim 14 or 15, characterized in that the third and / or fourth switching element (C, D) at least predominantly on the side of the main gearset (HS) is arranged on the also the assembly of the fifth and sixth switching element (E , F) is arranged [ 6 - 9 ]. Multi-stage automatic transmission according to one of claims 10 to 15, characterized in that the third and / or fourth switching element (C, D) at least partially radially above the main gearset (HS) or on the side of the main gearset (HS) is arranged, which Assembly of the fifth and sixth switching element (E, F) is opposite [ 4 + 5 + 10 + 11 ]. Multi-stage automatic transmission according to one of claims 10 to 17, characterized in that the first switching element (A) is arranged closer to the main gearset (HS) than the second switching element (B) [ 4 - 11 ]. Multi-stage automatic transmission according to one of claims 10 to 18, characterized in that the first switching element (A) axially directly adjacent to the main gearset (HS) on the Vorschaltradsatz (VS) side facing the Hauptradsatzes (HS) 4 - 11 ]. Multi-stage automatic transmission according to one of claims 1 to 19, characterized in that for the fifth and sixth switching element (E, F) common disc carrier (ZYLEF) as an inner disc carrier for the fifth switching element (E) and as outer disc carrier for the sixth switching element (F ) is trained [ 3 + 5 + 8th + 10 ]. Multi-stage automatic transmission according to claim 20, characterized in that the disk pack ( 500 ) of the fifth switching element (E) is arranged on a larger diameter than the plate pack ( 600 ) of the sixth switching element (F) [ 3 + 5 + 8th + 10 ]. Multi-stage automatic transmission according to claim 20 or 21, characterized in that the disk set ( 500 ) of the fifth switching element (E) seen spatially at least partially radially above the disk set ( 600 ) of the sixth switching element (F) is arranged. [ 3 + 5 + 8th + 10 ]. Multi-stage automatic transmission according to claim 20, 21 or 22, characterized in that the servos ( 510 . 610 ) of the fifth and sixth switching element (E, F) spatially seen are at least predominantly juxtaposed and substantially only by a lateral surface of the fifth and sixth switching element (E, F) common plate carrier (ZYLEF) are separated from each other 3 + 8th ]. Multi-stage automatic transmission according to one of claims 20 to 23, characterized in that a pressure chamber ( 611 ) of the servo device ( 610 ) of the sixth Schaltele Mentes (F) closer to the transfer gear (VS) or closer to the main gear (HS) is arranged as a pressure chamber ( 511 ) of the servo device ( 510 ) of the fifth switching element (E), wherein the pressure chamber ( 611 ) of the servo device ( 610 ) of the sixth switching element (F) only by a lateral surface of the fifth and sixth switching element (E, F) common disc carrier (ZYLEF) of the pressure compensation chamber ( 512 ) of the servo device ( 510 ) of the fifth switching element (E) is disconnected [ 3 + 8th ]. Multi-stage automatic transmission according to claim 20, 21 or 22, characterized in that the servo device ( 510 ) of the fifth switching element (E) seen spatially at least predominantly radially over the servo device ( 610 ) of the sixth switching element (F) is arranged and substantially only by a lateral surface of the fifth and sixth switching element (E, F) common disc carrier (ZYLEF) of this servo device ( 610 ) of the sixth switching element (F) is disconnected [ 5 + 10 ]. Multi-stage automatic transmission according to claim 25, characterized in that a pressure chamber ( 511 ) of the servo device ( 510 ) of the fifth switching element (E) seen spatially in a region radially above a pressure chamber ( 611 ) of the servo device ( 610 ) of the sixth switching element (F) is arranged, and / or that a pressure compensation chamber ( 512 ) of the servo device ( 510 ) of the fifth switching element (E) seen spatially in a region radially above a pressure equalization space ( 612 ) of the servo device ( 610 ) of the sixth switching element (F) is arranged [ 5 + 10 ]. Multi-stage automatic transmission according to one of claims 1 to 19, characterized in that for the fifth and sixth switching element (E, F) common plate carrier (ZYLEF) as outer disc carrier for the fifth switching element (E) and as an inner disc carrier for the sixth switching element (F ) is trained [ 2 + 4 + 6 + 7 ]. Multi-stage automatic transmission according to claim 27, characterized in that the disk set ( 600 ) of the sixth switching element (F) is arranged on a larger diameter than the plate pack ( 500 ) of the fifth switching element (E) [ 2 + 4 + 6 + 7 ]. Multi-stage automatic transmission according to claim 27 or 28, characterized in that the disk set ( 600 ) of the sixth switching element (F) seen spatially at least partially radially above the disk pack ( 500 ) of the fifth switching element (E) is arranged [ 2 + 4 + 6 + 7 ]. Multi-stage automatic transmission according to claim 27, 28 or 29, characterized in that the servos ( 510 . 610 ) of the fifth and sixth switching element (E, F) spatially seen are at least predominantly juxtaposed and substantially only by a lateral surface of the fifth and sixth switching element (E, F) common plate carrier (ZYLEF) are separated from each other 2 + 6 + 7 ]. Multi-stage automatic transmission according to one of claims 27 to 30, characterized in that a pressure chamber ( 511 ) of the servo device ( 510 ) of the fifth Schaltele Mentes (E) closer to the transfer gear (VS) or closer to the main gear (HS) is arranged as a pressure chamber ( 611 ) of the servo device ( 610 ) of the sixth switching element (F), wherein the pressure chamber ( 511 ) of the servo device ( 510 ) of the fifth switching element (E) only by a lateral surface of the fifth and sixth switching element (E, F) common disc carrier (ZYLEF) of the pressure compensation chamber ( 612 ) of the servo device ( 610 ) of the sixth switching element (F) is disconnected [ 2 + 6 + 7 ]. Multi-stage automatic transmission according to claim 27, 28 or 29, characterized in that the servo device ( 610 ) of the sixth switching element (F) seen spatially at least predominantly radially over the servo device ( 510 ) of the fifth switching element (E) is arranged and substantially only by a lateral surface of the fifth and sixth switching element (E, F) common plate carrier (ZYLEF) of this servo device ( 510 ) of the fifth switching element (E) is disconnected [ 4 ]. Multi-stage automatic transmission according to claim 32, characterized in that a pressure chamber ( 611 ) of the servo device ( 610 ) of the sixth switching element (F) seen spatially in a region radially above a pressure chamber ( 511 ) of the servo device ( 510 ) of the fifth switching element (E) is arranged, and / or that a pressure compensation chamber ( 612 ) of the servo device ( 610 ) of the sixth switching element (F) seen spatially in a region radially above a pressure equalization space ( 512 ) of the sero device ( 510 ) of the fifth switching element (E) is arranged [ 4 ]. Multi-stage automatic transmission according to one of Claims 1 to 19, characterized in that the plate carrier (ZYLEF) common to the fifth and sixth switching element (E, F) is designed as an outer plate carrier for the fifth and sixth switching element (E, F) [ 11 ]. Multi-stage automatic transmission according to claim 34, characterized in that the disk pack ( 500 ) of the fifth shift element (E) closer to the main gearset (HS) or closer to the transfer gear (VS) is arranged as the disk pack ( 600 ) of the sixth switching element (F) [ 11 ]. Multistage automatic transmission according to one of Claims 1 to 19, characterized in that the plate carrier (ZYLEF) common to the fifth and sixth shifting elements (E, F) is designed as an inner disk carrier for the fifth and sixth shifting elements (E, F) [ 12 ]. Multi-stage automatic transmission according to claim 36, characterized in that the disk pack ( 600 ) of the sixth shift element (F) is arranged closer to the main gearset (HS) or closer to the transfer gearset (VS) than the disk pack ( 500 ) of the fifth switching element (E) [ 12 ]. Multi-stage automatic transmission according to one of claims 34 to 37, characterized in that the disk packs ( 500 . 600 ) of the fifth and sixth switching elements (E, F) are arranged on an at least similar diameter [ 11 + 12 ]. Multi-stage automatic transmission according to one of claims 34 to 38, characterized in that the servo device ( 510 ) of the fifth switching element (E) seen spatially at least predominantly radially over the servo device ( 610 ) of the sixth switching element (F) is arranged and substantially only by a lateral surface of the fifth and sixth switching element (E, F) common plate carrier (ZYLEF) of this servo device ( 610 ) of the sixth switching element (F) is disconnected [ 11 ]. Multi-stage automatic transmission according to claim 39, characterized in that a pressure chamber ( 511 ) of the servo device ( 510 ) of the fifth switching element (E) seen spatially in a region radially above a pressure equalization space ( 612 ) of the servo device ( 610 ) of the sixth switching element (F) is arranged, and that a pressure compensation space ( 512 ) of the servo device ( 510 ) of the fifth switching element (E) seen spatially in a region radially above a pressure chamber ( 611 ) of the servo device ( 610 ) of the sixth switching element (F) is arranged [ 11 ]. Multi-stage automatic transmission according to one of claims 34 to 38, characterized in that the servo device ( 510 ) of the fifth shift element (E) seen spatially at least predominantly on the side facing away from the main gear (HS) side of the servo device ( 610 ) of the sixth switching element (F) is arranged and substantially only by a lateral surface of the fifth and sixth switching element (E, F) common plate carrier (ZYLEF) of this servo device ( 610 ) of the sixth switching element (F) is disconnected [ 12 ]. Multi-stage automatic transmission according to claim 41, characterized in that a pressure chamber ( 611 ) of the servo device ( 610 ) of the sixth shift element (F) closer to the main gearset (HS) is arranged as a pressure compensation chamber ( 612 ) of the servo device ( 610 ) of the sixth switching element (F), and / or that a pressure equalization space ( 512 ) of the servo device ( 510 ) of the fifth shift element (E) closer to the main gear (HS) is arranged as a pressure chamber ( 511 ) of the servo device ( 510 ) that of the fifth switching element (E) [ 12 ]. Multi-stage automatic transmission according to claim 41 or 42, characterized in that the pressure equalization spaces ( 512 . 612 ) of the servo device ( 510 . 610 ) of the fifth and sixth switching element (E, F) are separated from each other only by a lateral surface of the plate carrier (ZYLEF) common to the fifth and sixth switching element (E, F) [ 12 ]. Multi-stage automatic transmission according to one of claims 1 to 43, characterized in that the fifth and sixth shift element (E, F) common disc carrier (ZYLEF) on a gearbox fixed hub (GN) or on a gear housing fixed housing wall (GW) or on a gear housing fixed housing cover (GD) is rotatably mounted, wherein a pressure and / or lubricant supply ( 511 . 611 respectively. 512 . 612 ) to the servos ( 510 . 610 ) of the fifth and sixth switching element (E, F) in sections within this gearbox fixed hub (GN) or this housing wall (GW) or this housing cover (GD) extend [ 2 + 9 ]. Multi-stage automatic transmission according to one of claims 1 to 43, characterized in that for the fifth and sixth switching element (E, F) common plate carrier (ZYLEF) is rotatably mounted on the output shaft (AB), wherein a pressure and / or lubricant supply ( 511 . 611 respectively. 512 . 612 ) to the servos ( 510 . 610 ) of the fifth and sixth switching elements (E, F) run in sections within this output shaft (AB) [ 10 + 12 ]. Multi-stage automatic transmission according to one of claims 1 to 45, characterized in that the transfer gearset (VS), a sun gear (SO_VS), a ring gear (HO_VS) and a coupled web (ST_VS), on the inner and outer planetary gears (P1_VS, P2_VS) rotatable are mounted, wherein • the inner planetary gears (P1_VS) of the transfer gearset (VS) with the sun gear (SO VS) and the outer planetary gears (P2_VS) of the transfer gearset (VS) mesh, • the outer planetary gears (P2_VS) of the transfer gear (VS ) mesh with the inner planetary gears (P1_VS) and the ring gear (HO_VS) of the transfer gearset (HS), • the bridge (ST_VS) of the transfer gearset (VS) forms the input element of the transfer gearset (VS) permanently connected to the drive input shaft (AN), the ring gear (HO_VS) of the transfer gearset (VS) forms the output element of the transfer gearset (VS) that can be connected to input elements of the main gearset (HS) and • the sun gear (SO_VS) of the advance gear (VS) on the gear housing (GG) is fixed, and that the main gear (HS) as a two-track four Shaft gear is executed with two coupled single planetary gear sets, comprising two sun gears (S1_HS, S2_HS), two ring gears (H1_HS, H2_HS), a first web (ST1_HS), are rotatably mounted on the first planet gears (PL_HS), and a coupled second web (ST2_HS), are rotatably mounted on the inner and outer planet gears (PLi_HS, PLa_HS), wherein • the first planetary gears (PL_HS) of the main gearset (HS) with the first ring gear (H1_HS) and the first sun gear (S1_HS) of Main gearset (HS) mesh, • the inner planet gears (PLi_HS) of the main gearset (HS) with the outer planetary gears (PLa_HS) and the second sun gear (S2_HS) of the main gearset (HS) mesh, • the outer planetary gears (PLa_HS) of the main gearset (HS ) mesh with the inner planetary gears (PLi_HS) and the second ring gear (H2_HS) of the main gearset (HS), • the first sun gear (S1_HS) and the coupled second web (ST2_HS) of the main gearset (HS) are interconnected unden are and form the first input element of the main gearset (HS) and with the output elements ( 230 . 330 . 630 ) of the second, third and sixth switching element (B, C, F) are connected, • the second sun gear (S2_HS) of the main gearset (HS) forms the second input element of the main gearset (HS) and with the output element ( 130 ) of the first shift element (A) is connected, • the first web (ST1_HS) and the second ring gear (H2_HS) of the main gearset (HS) are interconnected and form the third input element of the main gearset (HS) and with the output elements ( 430 . 530 ) of the fourth and fifth shift elements (D, E) are connected, and • the first ring gear (H1_HS) of the main gearset (HS) forms the output element of the main gearset (HS) and is connected to the output shaft (AB) [ 10 + 11 ]. Multi-stage automatic transmission according to one of claims 1 to 45, characterized in that the transfer gear (VS) a sun gear (SO_VS), a ring gear (HO_VS) and a coupled web (ST_VS), on the inner and outer planet gears (P1_VS, P2_VS ) are rotatably mounted, wherein • the inner planet gears (P1_VS) of the transfer gearset (VS) with the sun gear (SO_VS) and the outer planet gears (P2_VS) of the transfer gearset (VS) mesh, • the outer planetary gears (P2_VS) of the transfer gearset (VS) meshing with the inner planetary gears (P1_VS) and the ring gear (HO_VS) of the transfer gearset (HS), • the land (ST_VS) of the transfer gearset (VS) forms the input element of the transfer gearset (VS) permanently connected to the drive input shaft (AN), Ring gear (HO_VS) of the Vorschaftradsatzes (VS) with the input elements of the main gearset (HS) connectable output element of the transfer gear (VS) forms and • the sun gear (SO_VS) of the Vorschaltra set (VS) is fixed to the transmission housing, and that the main gearset (HS) is designed as a reduced three-gear five-shaft transmission with three sun gears (S1_HS, S2_HS, S3_HS), a coupled ring gear (H13_HS), a second ring gear (H2_HS), a coupled web (ST13_HS) with long planetary gears rotatably mounted thereon (P13_HS), and a second web (ST2_HS) with short planetary gears rotatably mounted thereon (P2_HS), wherein • the first sun gear (S1_HS) of the main gearset (HS) axially between the second and third sun gear (S2_HS, S3_HS) of the main gearset (HS), • the long planetary gears (P13_HS) of the main gearset (HS) with the coupled ring gear (H13_HS) and the first and third sun gear (S1_HS, S3_HS) of the main gearset (HS ), • the short planetary gears (P2_HS) of the main gearset (HS) mesh with the second ring gear (H2_HS) and the second sun gear (S2_HS) of the main gearset (HS), • the first and second sun gears ( S1_HS, S2_HS) of the main gearset (HS) are fixedly connected to each other and form the first input element of the main gearset (HS) and with the output elements ( 230 . 630 ) of the second and sixth switching element (B, F) are connected, • the second ring gear (H2_HS) of the main gearset (HS) forms the second input element of the main gearset (HS) and with the output element ( 130 ) of the first shift element (A), • the coupled web (ST13_HS) of the main gearset (HS) forms the third input element of the main gearset (HS) and with the output elements ( 430 . 530 ) of the fourth and fifth shift element (D, E) is connected, • the third sun gear (S3_HS) of the main gearset (HS) forms a fourth input element of the main gearset (HS) and with the output element ( 330 ) of the third switching element (C) is connected, and • the coupled ring gear (H13_HS) and the second web (ST2_HS) of the main gearset (HS) are fixedly connected to each other and form the output element of the main gearset (HS) and to the output shaft (AB) are connected [ 2 + 5 ]. Multi-stage automatic transmission according to one of claims 1 to 45, characterized in that the transfer gear (VS) a sun gear (SO_VS), a ring gear (HO_VS) and a coupled web (ST_VS), on the inner and outer planet gears (P1_VS, P2_VS ) are rotatably mounted, wherein • the inner planet gears (P1_VS) of the pre-scarf tradsatzes (VS) with the sun gear (SO_VS) and the outer planetary gears (P2_VS) of the transfer gearset (VS) mesh, • the outer planetary gears (P2_VS) of the transfer gearset (VS) with the inner planetary gears (P1_VS) and the ring gear (HO_VS) of the • Intermediate gearset (HS) comb, • Stator (ST_VS) of the transfer gearset (VS) forms the input element of the transfer gearset (VS) permanently connected to the input shaft (AN), • The ring gear (HO_VS) of the transfer gearset (VS) with input elements of the main gearset (HS) connectable output element of the transfer gearset (VS) forms and • the sun gear (SO_VS) of the transfer gearset (VS) is fixed to the transmission housing, and that the main gearset (HS) is designed as a reduced three-way five-shaft transmission with three sun gears (S1_HS, S2_HS, S3_HS), a coupled ring gear (H13_HS), a second ring gear (H2_HS), a coupled web (ST13_HS) with long planetary gears rotatably mounted thereon (P13 _HS), as well as a second web (ST2_HS) with short planetary gears (P2_HS) rotatably mounted thereon, wherein • the first sun gear (S1_HS) of the main gearset (HS) axially between the second and third sun gear (S2_HS, S3_HS) of the main gearset (HS) • the long planetary gears (P13_HS) of the main gearset (HS) mesh with the coupled ring gear (H13_HS) and the first and third sun gears (S1_HS, S3_HS) of the main gearset (HS), • the short planetary gears (P2_HS) of the main gearset ( HS) with the second ring gear (H2_HS) and the second sun gear (S2_HS) of the main gearset (HS), • the first and second sun gear (S1_HS, S2_HS) of the main gearset (HS) are fixedly connected to each other and the first input element of the main gearset ( HS) and with the output element ( 230 ) of the second switching element (B) are connected, • the second ring gear (H2_HS) of the main gearset (HS) forms the second input element of the main gearset (HS) and with the output element ( 130 ) of the first shift element (A), • the coupled web (ST13_HS) of the main gearset (HS) forms the third input element of the main gearset (HS) and with the output elements ( 430 . 530 ) of the fourth and fifth shift element (D, E), • the third sun gear (S3_HS) of the main gearset (HS) forms a fourth input element of the main gearset (HS) and with the output elements ( 330 . 630 ) of the third and sixth switching element (C, F) is connected, and • the coupled ring gear (H13_HS) and the second web (ST2_HS) of the main gearset (HS) are firmly connected together and form the output element of the main gearset (HS) and with the Output shaft (AB) are connected [ 6 - 9 ]. Multi-stage automatic transmission according to claim 47 or 48, characterized in that the coupled web (ST13_HS) of the main gearset (HS) has a web plate which in the radial direction axially between the first and third sun gear (S1_HS, S3_HS) of the main gearset (HS) penetrates inside and with the output element ( 530 ) of the fifth switching element (E) is rotationally connected, wherein a hub of this web plate or one with this web plate and the output element ( 530 ) of the fifth switching element (E) rotationally connected web ( 540 ) either the first and second sun gear (S1_HS, S2_HS) of the main gearset (HS) or the third sun gear (S3_HS) of the main gearset (HS) penetrates centrically in the axial direction [ 2 - 9 ]. Multi-speed automatic transmission after one of the previous ones Claims, characterized in that by selectively closing the Switching elements (A to F) at least eight forward gears are so switchable that an input speed of the drive shaft (AN) on the Output shaft (AB) transferable is that to switch from one gear to the next higher or higher next following lower gear from the currently operated switching elements respectively only one switching element opened and another switching element is closed, in which • in one first forward the first and fourth switching elements (A, D), • in a second forward gear the first and third switching elements (A, C), • in a third forward gear the first and second switching elements (A, B), • in a fourth forward gear the first and sixth switching elements (A, F), • in one fifth forward gear the first and fifth switching element (A, E), • in a sixth forward speed the fifth and sixth switching element (E, F), • in a seventh forward gear the second and fifth Switching element (B, E), • in an eighth forward gear the third and fifth switching element (C, E) are closed, and / or being in a reverse gear the fourth switching element (D) and additionally either the second Switching element (B) or the sixth switching element (F) closed are.